US LAWS, STATUTES & CODES ON-LINE

[47 FR 34526, Aug. 10, 1982; 48 FR 13013, Mar. 29, 1983, as amended at 54 FR 36240, Aug. 31, 1989; 54 FR 38788, Sept. 20, 1989; 62 FR 47539, 47540, Sept. 9, 1997; 68 FR 10960, Mar. 7, 2003]

1. Definitions.

1.1  “HRF–1–1979” means the Association of Home Appliance Manufacturers standard for household refrigerators, combination refrigerators-freezers, and household freezers, also approved as an American National Standard as a revision of ANSI B38.1–1970.

1.2  “Anti-sweat heater” means a device incorporated into the design of a freezer to prevent the accumulation of moisture on exterior surfaces of the cabinet under conditions of high ambient humidity.

1.3  “Cycle” means the period of 24 hours for which the energy use of a freezer is calculated as though the consumer-activated compartment temperature controls were preset so that the desired compartment temperatures were maintained.

1.4  “Cycle type” means the set of test conditions having the calculated effect of operating a freezer for a period of 24 hours with the consumer-activated controls other than the compartment temperature control set to establish various operating characteristics.

1.5  “Standard cycle” means the cycle type in which the anti-sweat heater switch, when provided, is set in the highest energy consuming position.

1.6  “Adjusted total volume” means the product of, (1) the freezer volume as defined in HRF–1–1979 in cubic feet, times (2) an adjustment factor.

1.7  “Automatic Defrost” means a system in which the defrost cycle is automatically initiated and terminated, with resumption of normal refrigeration at the conclusion of defrost operation. The system automatically prevents the permanent formation of frost on all refrigerated surfaces. Nominal refrigerated food temperatures are maintained during the operation of the automatic defrost system.

1.8  “Long-time Automatic Defrost” means an automatic defrost system where successive defrost cycles are separated by 14 hours or more of compressor-operating time.

1.9  “Stabilization Period” means the total period of time during which steady-state conditions are being attained or evaluated.

1.10  “Variable defrost control” means a long-time automatic defrost system (except the 14-hour defrost qualification does not apply) where successive defrost cycles are determined by an operating condition variable or variables other than solely compressor operating time. This includes any electrical or mechanical device. Demand defrost is a type of variable defrost control.

1.11  “Quick freeze” means an optional feature on freezers which is initiated manually and shut off manually. It bypasses the thermostat control and places the compressor in a steady-state operating condition until it is shut off.

2. Test Conditions.

2.1  Ambient temperature. The ambient temperature shall be 90.0±1.0 °F. (32.2±0.6 °C.) during the stabilization period and during the test period. The ambient temperature shall be 80±2 °F dry bulb and 67 °F wet bulb during the stabilization period and during the test period when the unit is tested in accordance with section 3.3.

2.2  Operational conditions. The freezer shall be installed and its operating conditions maintained in accordance with HRF–1–1979, section 7.2 through section 7.4.3.3, except that the vertical ambient gradient at locations 10 inches (25.4 cm) out from the centers of the two sides of the unit being tested is to be maintained during the test. Unless the area is obstructed by shields or baffles, the gradient is to be maintained from 2 inches (5.1 cm) above the floor or supporting platform to a height one foot (30.5 cm) above the unit under test. Defrost controls are to be operative and the anti-sweat heater switch is to be “on” during one test and “off” during a second test. The quick freeze option shall be switched off unless specified.

2.3  Steady State Condition. Steady state conditions exist if the temperature measurements taken at four minute intervals or less during a stabilization period are not changing at a rate greater than 0.042 °F. (0.023 °C.) per hour as determined by the applicable condition of A or B.

A—The average of the measurements during a two hour period if no cycling occurs or during a number of complete repetitive compressor cycles through a period of no less than two hours is compared to the average over an equivalent time period with three hours elapsed between the two measurement periods.

B—If A above cannot be used, the average of the measurements during a number of complete repetitive compressor cycles through a period of no less than two hours and including the last complete cycle prior to a defrost period, or if no cycling occurs, the average of the measurements during the last two hours prior to a defrost period; are compared to the same averaging period prior to the following defrost period.

3. Test Control Settings.

3.1  Model with no user operable temperature control. A test shall be performed during which the compartment temperature and energy use shall be measured. A second test shall be performed with the temperature control electrically short circuited to cause the compressor to run continuously. If the model has the quick freeze option, it is to be used to bypass the temperature control.

3.2  Model with user operable temperature control. Testing shall be performed in accordance with one of the following sections using the standardized temperature of 0.0 °F. (−17.8 °C.). Variable defrost control models shall achieve 0±2 °F during the steady-state conditions prior to the optional test with no door openings.

3.2.1  A first test shall be performed with all temperature controls set at their median position midway between their warmest and coldest settings. Knob detents shall be mechanically defeated if necessary to attain a median setting. A second test shall be performed with all controls set at either their warmest or their coldest setting (not electrically or mechanically bypassed), whichever is appropriate, to attempt to achieve compartment temperatures measured during the two tests which bound (i.e., one is above and one is below) the standardized temperature. If the compartment temperatures measured during these two tests bound the standardized temperature, then these test results shall be used to determine energy consumption. If the compartment temperature measured with all controls set at their coldest setting is above the standardized temperature, a third test shall be performed with all controls set at their warmest setting and the result of this test shall be used with the result of the test performed with all controls set at their coldest setting to determine energy consumption. If the compartment temperature measured with all controls set at their warmest setting is below the standardized temperature; then the result of this test alone will be used to determine energy consumption.

3.2.2  Alternatively, a first test may be performed with all temperature controls set at their warmest setting. If the compartment temperature is below the standardized temperature, then the result of this test alone will be used to determine energy consumption. If the above condition is not met, then the unit shall be tested in accordance with 3.2.1 above.

3.2.3  Alternatively, a first test may be performed with all temperature controls set at their coldest setting. If the compartment temperature is above the standardized temperature, a second test shall be performed with all controls set at their warmest setting and the results of these two tests shall be used to determine energy consumption. If the above condition is not met, then the unit shall be tested in accordance with 3.2.1 above.

3.3 Variable defrost control optional test. After a steady-state condition is achieved, the door-opening sequence is initiated with an 18±2 second freezer door-opening occurring every eight hours to obtain three door-openings per 24-hour period. The first freezer door-opening shall occur at the initiation of the test period. The door(s) are to be opened 60 to 90°with an average velocity for the leading edge of the door of approximately two feet per second. Prior to the initiation of the door-opening sequence, the freezer defrost control mechanism may be re-initiated in order to minimize the test duration.

4. Test Period.

4.1  Test Period. Tests shall be performed by establishing the conditions set forth in Section 2 and using control settings as set forth in Section 3 above.

4.1.1  Nonautomatic Defrost. If the model being tested has no automatic defrost system, the test time period shall start after steady state conditions have been achieved, and be of not less than three hours' duration. During the test period the compressor motor shall complete two or more whole cycles (a compressor cycle is a complete “on” and a complete “off” period of the motor). If no “off” cycling will occur, as determined during the stabilization period, the test period shall be three hours. If incomplete cycling (less than two compressor cycles) occurs during a 24 hour period, the results of the 24 hour period shall be used.

4.1.2  Automatic Defrost. If the model being tested has an automatic defrost system, the test time period shall start after steady state conditions have been achieved and be from one point during a defrost period to the same point during the next defrost period. If the model being tested has a long-time automatic defrost system, the alternate provisions of 4.1.2.1 may be used. If the model being tested has a variable defrost control the provisions of 4.1.2.2. shall apply.

4.1.2.1  Long-time Automatic Defrost. If the model being tested has a long-time automatic defrost system, the test time period may consist of two parts. A first part would be the same as the test for a unit having no defrost provisions (section 4.1.1). The second part would start when a defrost period is initiated during a compressor “on” cycle and terminate at the second turn “on” of the compressor motor or after four hours, whichever comes first.

4.1.2.2 Variable defrost control. If the model being tested has a variable defrost control system, the test shall consist of three parts. Two parts shall be the same as the test for long-time automatic defrost in accordance with section 4.1.2.1 above. The third part is the optional test to determine the time between defrosts (5.2.1.3). The third part is used by manufacturers that choose not to accept the default value of F of 0.20, to calculate CT.

4.1.2.3 Variable defrost control optional test. After steady-state conditions with no door-openings are achieved in accordance with section 3.3 above, the test is continued using the above daily door-opening sequence until stabilized operation is achieved. Stabilization is defined as a minimum of three consecutive defrost cycles with times between defrost that will allow the calculation of a Mean Time Between Defrosts (MTBD1) that satisfies the statistical relationship of 90 percent confidence. The test is repeated on at least one more unit of the model and until the Mean Time Between Defrosts for the multiple unit test (MTBD2) satisfies the statistical relationship. If the time between defrosts is greater than 96 hours (compressor “on” time) and this defrost period can be repeated on a second unit, the test may be terminated at 96 hours (CT) and the absolute time value used for MTBD for each unit.

5. Test Measurements.

5.1  Temperature Measurements. Temperature measurements shall be made at the locations prescribed in Figure 7–2 of HRF–1–1979 and shall be accurate to within ±0.5 °F. (0.3 °C.) of true value.

5.1.1  Measured Temperature. The measured temperature is to be the average of all sensor temperature readings taken at a particular time. Measurements shall be taken at regular intervals not to exceed four minutes.

5.1.2  Compartment Temperature. The compartment temperature for each test period shall be an average of the measured temperatures taken during a complete cycle or several complete cycles of the compressor motor (one compressor cycle is one complete motor “on” and one complete motor “off” period). For long-time automatic defrost models, compartment temperature shall be that measured in the first part of the test period specified in 4.1.1. For models equipped with variable defrost controls, compartment temperatures shall be those measured in the first part of the test period specified in 4.1.2.2.

5.1.2.1  The number of complete compressor motor cycles over which the measured temperatures in a compartment are to be averaged to determine compartment temperature shall be equal to the number of minutes between measured temperature readings rounded up to the next whole minute or a number of complete cycles over a time period exceeding one hour. One of the cycles shall be the last complete compressor motor cycles during the test period.

5.1.2.2  If no compressor motor cycling occurs, the compartment temperature shall be the average of the measured temperatures taken during the last thirty-two minutes of the test period.

5.1.2.3  If incomplete cycling occurs (less than one cycle) the compartment temperature shall be the average of all readings taken during the last three hours of the last complete “on” period.

5.2  Energy Measurements:

5.2.1  Per-day Energy Consumption. The energy consumption in kilowatt-hours per day for each test period shall be the energy expended during the test period as specified in section 4.1 adjusted to a 24 hour period.

The adjustment shall be determined as follows:

5.2.1.1  Nonautomatic and automatic defrost models. The energy consumption in kilowatt-hours per day shall be calculated equivalent to:

ET=(EP×1440× K)/T where

ET=test cycle energy expended in kilowatt-hours per day,

EP=energy expended in kilowatt-hours during the test period.

T=length of time of the test period in minutes,

1440=conversion factor to adjust to a 24 hour period in minutes per day, and

K=correction factor of 0.7 for chest freezers and 0.85 for upright freezers to adjust for average household usage, dimensionless.

5.2.1.2  Long-time Automatic Defrost. If the two part test method is used, the energy consumption in kilowatt-hours per day shall be calculated equivalent to:

ET=(1440× K× EP1/T1) + ((EP2−(EP1× T2/T1))× K×12/CT)

where

ET, 1440, and K are defined in 5.2.1.1

EP1=energy expended in kilowatt-hours during the first part of the test.

EP2=energy expended in kilowatt-hours during the second part of the test,

CT=Defrost timer run time in hours required to cause it to go through a complete cycle, to the nearest tenth hour per cycle,

12=conversion factor to adjust for a 50% run time of the compressor in hours per day, and

T1 and T2=length of time in minutes of the first and second test parts respectively.

5.2.1.3 Variable defrost control. The energy consumption in kilowatt-hours per day shall be calculated equivalent to:

ET=(1440 × EP1/T1) + (EP2 − (EP1 × T2/T1) × (12/CT) where 1440 is defined in 5.2.1.1 and EP1, EP2, T1, T2 and 12 are defined in 5.2.1.2.

CT=(CT_L × CT_M)/(Fx (CT_M − CT_L) + CT_L)

where:

CT_L=least or shortest time between defrost in tenths of an hour (greater than or equal to 6 hours but less than or equal to 12 hours, 6 ≤ _L ≤ 12)

CT_M=maximum time between defrost cycles in tenths of an hour (greater than CT_L but not more than 96 hours, CT_L ≤ CT_M ≤ 96)

F=ratio of per day energy consumption in excess of the least energy and the maximum difference in per day energy consumption and is equal to

F=(1/CT − 1/CT_M)/(1/CT_L − 1/CT_M) = (ET − ET_L)/(ET_M − ET_L) or 0.20 in lieu of testing to find CT

ET_L=least electrical energy consumed, in kilowatt hours

ET_M=maximum electrical energy consumed, in kilowatt hours

For demand defrost models with no values for CT_L and CT_M in the algorithm the default values of 12 and 84 shall be used, respectively.

5.2.1.4 Variable defrost control optional test. Perform the optional test for variable defrost control models to find CT.

CT=MTBD × 0.5

MTBD=mean time between defrost

X=time between defrost cycles

N=number of defrost cycles

5.3  Volume measurements. The total refrigerated volume, VT, shall be measured in accordance with HRF–1–1979, section 3.20 and section 5.1 through 5.3.

6. Calculation of Derived Results From Test Measurements.

6.1  Adjusted Total Volume. The adjusted total volume, VA, for freezers under test shall be defined as:

VA=VT× CF

where

VA=adjusted total volume in cubic feet,

VT=total refrigerated volume in cubic feet, and

CF=Correction factor of 1.73, dimensionless.

6.2  Average Per Cycle Energy Consumption:

6.2.1  The average per-cycle energy consumption for a cycle type is expressed in kilowatt-hours per cycle to the nearest one hundredth (0.01) kilowatt-hour and shall depend upon the compartment temperature attainable as shown below.

6.2.1.1  If the compartment temperature is always below 0.0 °F. (−17.8 °C.), the average per-cycle energy consumption shall be equivalent to:

E=ET1

where

E=Total per-cycle energy consumption in kilowatt-hours per day.

ET is defined in 5.2.1, and

Number 1 indicates the test period during which the highest compartment temperature is measured.

6.2.1.2  If one of the compartment temperatures measured for a test period is greater than 0.0 °F. (17.8 °C.), the average per-cycle energy consumption shall be equivalent to:

E=ET1+((ET2−ET1)×(0.0−TF1)/(TF2−TF1))

where

E is defined in 6.2.1.1

ET is defined in 5.2.1

TF=compartment temperature determined according to 5.1.2 in degrees F.

Numbers 1 and 2 indicate measurements taken during the first and second test period as appropriate, and

0.0=Standardized compartment temperature in degrees F.

[47 FR 34528, Aug. 10, 1982; 48 FR 13013, Mar. 29, 1983, as amended at 54 FR 36241, Aug. 31, 1989; 54 FR 38788, Sept. 20, 1989]

The provisions of this Appendix C shall apply to products manufactured after September 29, 2003. The restriction on representations concerning energy use or efficiency in 42 U.S.C. 6293(c)(2) shall apply on February 25, 2004.

1.  Definitions

1.1  AHAM means the Association of Home Appliance Manufacturers.

1.2  Compact dishwasher means a dishwasher that has a capacity of less than eight place settings plus six serving pieces as specified in ANSI/AHAM DW–1 (see §430.22), using the test load specified in section 2.7 of this Appendix.

1.3  Cycle means a sequence of operations of a dishwasher which performs a complete dishwashing function, and may include variations or combinations of washing, rinsing, and drying.

1.4  Cycle type means any complete sequence of operations capable of being preset on the dishwasher prior to the initiation of machine operation.

1.5  Non-soil-sensing dishwasher means a dishwasher that does not have the ability to adjust automatically any energy consuming aspect of a wash cycle based on the soil load of the dishes.

1.6  Normal cycle means the cycle type recommended by the manufacturer for completely washing a full load of normally soiled dishes including the power-dry feature.

1.7  Power-dry feature means the introduction of electrically generated heat into the washing chamber for the purpose of improving the drying performance of the dishwasher.

1.8  Preconditioning cycle means any cycle that includes a fill, circulation, and drain to ensure that the water lines and sump area of the pump are primed.

1.9  Sensor heavy response means, for standard dishwashers, the set of operations in a soil-sensing dishwasher for completely washing a load of dishes, four place settings of which are soiled according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22). For compact dishwashers, this definition is the same, except that two soiled place settings are used instead of four.

1.10  Sensor light response means, for both standard and compact dishwashers, the set of operations in a soil-sensing dishwasher for completely washing a load of dishes, one place setting of which is soiled with half of the gram weight of soils for each item specified in a single place setting according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22).

1.11  Sensor medium response means, for standard dishwashers, the set of operations in a soil-sensing dishwasher for completely washing a load of dishes, two place settings of which are soiled according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22). For compact dishwashers, this definition is the same, except that one soiled place setting is used instead of two.

1.12  Soil-sensing dishwasher means a dishwasher that has the ability to adjust any energy consuming aspect of a wash cycle based on the soil load of the dishes.

1.13  Standard dishwasher means a dishwasher that has a capacity equal to or greater than eight place settings plus six serving pieces as specified in ANSI/AHAM DW–1 (Incorporated by reference, see §430.22), using the test load specified in section 2.7 of this Appendix.

1.14  Standby mode means the lowest power consumption mode which cannot be switched off or influenced by the user and that may persist for an indefinite time when the dishwasher is connected to the main electricity supply and used in accordance with the manufacturer's instructions.

1.15  Truncated normal cycle means the normal cycle interrupted to eliminate the power-dry feature after the termination of the last rinse operation.

1.16  Truncated sensor heavy response means the sensor heavy response interrupted to eliminate the power-dry feature after the termination of the last rinse operation.

1.17  Truncated sensor light response means the sensor light response interrupted to eliminate the power-dry feature after the termination of the last rinse operation.

1.18  Truncated sensor medium response means the sensor medium response interrupted to eliminate the power-dry feature after the termination of the last rinse operation.

1.19  Water-heating dishwasher means a dishwasher which, as recommended by the manufacturer, is designed for heating cold inlet water (nominal 50 °F) or designed for heating water with a nominal inlet temperature of 120 °F. Any dishwasher designated as water-heating (50 °F or 120 °F inlet water) must provide internal water heating to above 120 °F in at least one wash phase of the normal cycle.

2.  Testing conditions:

2.1  Installation Requirements. Install the dishwasher according to the manufacturer's instructions. A standard or compact under-counter or under-sink dishwasher must be tested in a rectangular enclosure constructed of nominal 0.374 inch (9.5 mm) plywood painted black. The enclosure must consist of a top, a bottom, a back, and two sides. If the dishwasher includes a counter top as part of the appliance, omit the top of the enclosure. Bring the enclosure into the closest contact with the appliance that the configuration of the dishwasher will allow.

2.2  Electrical energy supply.

2.2.1  Dishwashers that operate with an electrical supply of 115 volts. Maintain the electrical supply to the dishwasher at 115 volts ±2 percent and within 1 percent of the nameplate frequency as specified by the manufacturer.

2.2.2  Dishwashers that operate with an electrical supply of 240 volts. Maintain the electrical supply to the dishwasher at 240 volts ±2 percent and within 1 percent of its nameplate frequency as specified by the manufacturer.

2.3  Water temperature. Measure the temperature of the water supplied to the dishwasher using a temperature measuring device as specified in section 3.1 of this Appendix.

2.3.1  Dishwashers to be tested at a nominal 140 °F inlet water temperature. Maintain the water supply temperature at 140° ±2 °F.

2.3.2  Dishwashers to be tested at a nominal 120 °F inlet water temperature. Maintain the water supply temperature at 120° ±2 °F.

2.3.3  Dishwashers to be tested at a nominal 50 °F inlet water temperature. Maintain the water supply temperature at 50° ±2 °F.

2.4  Water pressure. Using a water pressure gauge as specified in section 3.4 of this Appendix, maintain the pressure of the water supply at 35 ±2.5 pounds per square inch gauge (psig) when the water is flowing.

2.5  Ambient and machine temperature. Using a temperature measuring device as specified in section 3.1 of this Appendix, maintain the room ambient air temperature at 75° ±5 °F, and ensure that the dishwasher and the test load are at room ambient temperature at the start of each test cycle.

2.6  Test Cycle and Load.

2.6.1  Non-soil-sensing dishwashers to be tested at a nominal inlet temperature of 140 °F. These units must be tested on the normal cycle and truncated normal cycle without a test load if the dishwasher does not heat water in the normal cycle.

2.6.2  Non-soil-sensing dishwashers to be tested at a nominal inlet temperature of 50 °F or 120 °F. These units must be tested on the normal cycle with a clean load of eight place settings plus six serving pieces, as specified in section 2.7 of this Appendix. If the capacity of the dishwasher, as stated by the manufacturer, is less than eight place settings, then the test load must be the stated capacity.

2.6.3  Soil-sensing dishwashers to be tested at a nominal inlet temperature of 50 °F, 120 °F, or 140 °F. These units must be tested first for the sensor heavy response, then tested for the sensor medium response, and finally for the sensor light response with the following combinations of soiled and clean test loads.

2.6.3.1  For tests of the sensor heavy response, as defined in section 1.9 of this Appendix:

(A) For standard dishwashers, the test unit is to be loaded with a total of eight place settings plus six serving pieces as specified in section 2.7 of this Appendix. Four of the eight place settings must be soiled according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22) while the remaining place settings, serving pieces, and all flatware are not soiled.

(B) For compact dishwashers, the test unit is to be loaded with four place settings plus six serving pieces as specified in section 2.7 of this Appendix. Two of the four place settings must be soiled according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22) while the remaining place settings, serving pieces, and all flatware are not soiled.

2.6.3.2  For tests of the sensor medium response, as defined in section 1.11 of this Appendix:

(A) For standard dishwashers, the test unit is to be loaded with a total of eight place settings plus six serving pieces as specified in section 2.7 of this Appendix. Two of the eight place settings must be soiled according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22) while the remaining place settings, serving pieces, and all flatware are not soiled.

(B) For compact dishwashers, the test unit is to be loaded with four place settings plus six serving pieces as specified in section 2.7 of this Appendix. One of the four place settings must be soiled according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22) while the remaining place settings, serving pieces and all flatware are not soiled.

2.6.3.3  For tests of the sensor light response, as defined in section 1.10 of this Appendix:

(A) For standard dishwashers, the test unit is to be loaded with a total of eight place settings plus six serving pieces as specified in section 2.7 of this Appendix. One of the eight place settings must be soiled with half of the soil load specified for a single place setting according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22) while the remaining place settings, serving pieces, and all flatware are not soiled.

(B) For compact dishwashers, the test unit is to be loaded with four place settings plus six serving pieces as specified in section 2.7 of this Appendix. One of the four place settings must be soiled with half of the soil load specified for a single place setting according to the ANSI/AHAM DW–1 (Incorporated by reference, see §430.22) while the remaining place settings, serving pieces, and all flatware are not soiled.

2.7  Test Load.

2.8  Detergent. Use half the quantity of detergent specified according to ANSI/AHAM DW–1 (Incorporated by reference, see §430.22).

2.9  Testing requirements. Provisions in this Appendix pertaining to dishwashers that operate with a nominal inlet temperature of 50 °F or 120 °F apply only to water-heating dishwashers as defined in section 1.19 of this Appendix.

2.10  Preconditioning requirements. Precondition the dishwasher by establishing the testing conditions set forth in sections 2.1 through 2.5 of this Appendix. Set the dishwasher to the preconditioning cycle as defined in section 1.8 of this Appendix, without using a test load, and initiate the cycle.

3.  Instrumentation

Test instruments must be calibrated annually.

3.1  Temperature measuring device. The device must have an error no greater than ±1 °F over the range being measured.

3.2  Timer. Time measurements for each monitoring period shall be accurate to within 2 seconds.

3.3  Water meter. The water meter must have a resolution of no larger than 0.1 gallons and a maximum error no greater than ±1.5 percent of the measured flow rate for all water temperatures encountered in the test cycle.

3.4  Water pressure gauge. The water pressure gauge must have a resolution of one pound per square inch (psi) and must have an error no greater than 5 percent of any measured value over the range of 35 ±2.5 psig.

3.5  Watt-hour meter. The watt-hour meter must have a resolution of 1 watt-hour or less and a maximum error of no more than 1 percent of the measured value for any demand greater than 50 watts.

3.6  Standby wattmeter. The standby wattmeter must have a resolution of 0.1 watt or less, a maximum error of no more than 1 percent of the measured value, and must be capable of operating within the stated tolerances for input voltages up to 5 percent total harmonic distortion. The standby wattmeter must be capable of operating at frequencies from 47 hertz through 63 hertz. Power measurements must have a crest factor of 3 or more at currents of 2 amps RMS or less.

3.7  Standby watt-hour meter. The standby watt-hour meter must meet all the requirements of the standby wattmeter and must accumulate watt-hours at a minimum power level of 20 milliwatts.

4.  Test Cycle and Measurements

4.1  Test cycle. Perform a test cycle by establishing the testing conditions set forth in section 2 of this Appendix, setting the dishwasher to the cycle type to be tested, initiating the cycle, and allowing the cycle to proceed to completion.

4.2  Machine electrical energy consumption. Measure the machine electrical energy consumption, M, expressed as the number of kilowatt-hours of electricity consumed by the machine during the entire test cycle, using a water supply temperature as set forth in section 2.3 of this Appendix and using a watt-hour meter as specified in section 3.5 of this Appendix.

4.3  Water consumption. Measure the water consumption, V, expressed as the number of gallons of water delivered to the machine during the entire test cycle, using a water meter as specified in section 3.3 of this Appendix.

4.4  Standby power. Connect the dishwasher to a standby wattmeter or a standby watt-hour meter as specified in sections 3.6 and 3.7, respectively, of this Appendix. Select the conditions necessary to achieve operation in the standby mode as defined in section 1.14 of this Appendix. Monitor the power consumption but allow the dishwasher to stabilize for at least 5 minutes. Then monitor the power consumption for at least an additional 5 minutes. If the power level does not change by more than 5 percent from the maximum observed value during the later 5 minutes and there is no cyclic or pulsing behavior of the load, the load can be considered stable. For stable operation, standby power, S_m, can be recorded directly from the standby watt meter in watts or accumulated using the standby watt-hour meter over a period of at least 5 minutes. For unstable operation, the energy must be accumulated using the standby watt-hour meter over a period of at least 5 minutes and must capture the energy use over one or more complete cycles. Calculate the average standby power, S_m, expressed in watts by dividing the accumulated energy consumption by the duration of the measurement period.

5.  Calculation of Derived Results From Test Measurements

5.1  Machine energy consumption.

5.1.1  Machine energy consumption for non-soil-sensing electric dishwashers. Take the value recorded in section 4.2 of this Appendix as the per-cycle machine electrical energy consumption. Express the value, M, in kilowatt-hours per cycle.

5.1.2  Machine energy consumption for soil-sensing electric dishwashers. The machine energy consumption for the sensor normal cycle, M, is defined as:

M = (M_hr×F_hr) + (M_mr×F_mr) + (M_lr×F_lr)

where,

M_hr = the value recorded in section 4.2 of this Appendix for the test of the sensor heavy response, expressed in kilowatt-hours per cycle,

M_mr = the value recorded in section 4.2 of this Appendix for the test of the sensor medium response, expressed in kilowatt-hours per cycle,

M_lr = the value recorded in section 4.2 of this Appendix for the test of the sensor light response, expressed in kilowatt-hours per cycle,

F_hr = the weighting factor based on consumer use of heavy response = 0.05,

F_mr = the weighting factor based on consumer use of medium response = 0.33,

F_lr = the weighting factor based on consumer use of light response = 0.62.

5.2  Drying energy.

5.2.1  Drying energy consumption for non-soil-sensing electric dishwashers. Calculate the amount of energy consumed using the power-dry feature after the termination of the last rinse option of the normal cycle. Express the value, E_D, in kilowatt-hours per cycle.

5.2.2  Drying energy consumption for soil-sensing electric dishwashers. The drying energy consumption, E_D, for the sensor normal cycle is defined as:

E_D = (E_Dhr + E_Dmr + E_Dlr)/3

Where,

E_Dhr = energy consumed using the power-dry feature after the termination of the last rinse option of the sensor heavy response, expressed in kilowatt-hours per cycle,

E_Dmr = energy consumed using the power-dry feature after the termination of the last rinse option of the sensor medium response, expressed in kilowatt-hours per cycle,

E_Dlr = energy consumed using the power-dry feature after the termination of the last rinse option of the sensor light response, expressed in kilowatt-hours per cycle.

5.3  Water consumption.

5.3.1  Water consumption for non-soil-sensing dishwashers using electrically heated, gas-heated, or oil-heated water.

Take the value recorded in section 4.3 of this Appendix as the per-cycle water energy consumption. Express the value, V, in gallons per cycle.

5.3.2  Water consumption for soil-sensing dishwashers using electrically heated, gas-heated, or oil-heated water.

The water consumption for the sensor normal cycle, V, is defined as:

V = (V_hr×F_hr) + (V_mr×F_mr) + (V_lr×F_lr)

Where,

V_hr = the value recorded in section 4.3 of this Appendix for the test of the sensor heavy response, expressed in gallons per cycle,

V_mr = the value recorded in section 4.3 of this Appendix for the test of the sensor medium response, expressed in gallons per cycle,

V_lr = the value recorded in section 4.3 of this Appendix for the test of the sensor light response, expressed in gallons per cycle,

F_hr = the weighting factor based on consumer use of heavy response = 0.05,

F_mr = the weighting factor based on consumer use of medium response = 0.33,

F_lr = the weighting factor based on consumer use of light response = 0.62.

5.4  Water energy consumption for non-soil-sensing or soil-sensing dishwashers using electrically heated water.

5.4.1  Dishwashers that operate with a nominal 140 °F inlet water temperature, only. For the normal and truncated normal test cycle, calculate the water energy consumption, W, expressed in kilowatt-hours per cycle and defined as:

W = V×T×K

Where,

V = water consumption in gallons per cycle, as determined in section 5.3.1 of this Appendix,

T = nominal water heater temperature rise = 90 °F,

K = specific heat of water in kilowatt-hours per gallon per degree Fahrenheit = 0.0024.

5.4.2  Dishwashers that operate with a nominal inlet water temperature of 120 °F. For the normal and truncated normal test cycle, calculate the water energy consumption, W, expressed in kilowatt-hours per cycle and defined as:

W = V×T×K

Where,

V = water consumption in gallons per cycle, as determined in section 5.3.1 of this Appendix,

T = nominal water heater temperature rise = 70 °F,

K = specific heat of water in kilowatt-hours per gallon per degree Fahrenheit = 0.0024.

5.5  Water energy consumption per cycle using gas-heated or oil-heated water.

5.5.1  Dishwashers that operate with a nominal 140 °F inlet water temperature, only.

For each test cycle, calculate the water energy consumption using gas-heated or oil-heated water, W_g, expressed in Btu's per cycle and defined as:

W_g = V×T×C/e

Where,

V = reported water consumption in gallons per cycle, as determined in section 5.3.2 of this Appendix,

T = nominal water heater temperature rise = 90 °F,

C = specific heat of water in Btu's per gallon per degree Fahrenheit = 8.2,

e = nominal gas or oil water heater recovery efficiency = 0.75.

5.5.2  Dishwashers that operate with a nominal inlet water temperature of 120 °F. For each test cycle, calculate the water energy consumption using gas heated or oil heated water, W_g, expressed in Btu's per cycle and defined as:

Wg = V×T×C/e

Where,

V = reported water consumption in gallons per cycle, as determined in section 5.3.2 of this Appendix,

T = nominal water heater temperature rise = 70 °F,

C = specific heat of water in Btu's per gallon per degree Fahrenheit = 8.2,

e = nominal gas or oil water heater recovery efficiency = 0.75.

5.6  Annual standby energy consumption. Calculate the estimated annual standby energy consumption. First determine the number of standby hours per year, H_s, defined as:

H_s = H−(N×L).

Where,

H = the total number of hours per year = 8766 hours per year,

N = the representative average dishwasher use of 215 cycles per year,

L = the average of the duration of the normal cycle and truncated normal cycle, for non-soil-sensing dishwashers with a truncated normal cycle; the duration of the normal cycle, for non-soil-sensing dishwashers without a truncated normal cycle; the average duration of the sensor light response, truncated sensor light response, sensor medium response, truncated sensor medium response, sensor heavy response, and truncated sensor heavy response, for soil-sensing dishwashers with a truncated cycle option; the average duration of the sensor light response, sensor medium response, and sensor heavy response, for soil-sensing dishwashers without a truncated cycle option.

Then calculate the estimated annual standby power use, S, expressed in kilowatt-hours per year and defined as:

S = S_m×((H_s)/1000)

Where,

S_m = the average standby power in watts as determined in section 4.4 of this Appendix.

[68 FR 51900, Aug. 29, 2003]

1. Definitions

1.1  “AHAM” means the Association of Home Appliance Manufacturers.

1.2  “Bone dry” means a condition of a load of test clothes which has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed and weighed before cool down, and then dried again for 10-minute periods until the final weight change of the load is 1 percent or less.

1.3  “Compact” or compact size” means a clothes dryer with a drum capacity of less than 4.4 cubic feet.

1.4  “Cool down” means that portion of the clothes drying cycle when the added gas or electric heat is terminated and the clothes continue to tumble and dry within the drum.

1.5  “Cycle” means a sequence of operation of a clothes dryer which performs a clothes drying operation, and may include variations or combinations of the functions of heating, tumbling and drying.

1.6  “Drum capacity” means the volume of the drying drum in cubic feet.

1.7  “HLD–1” means the test standard promulgated by AHAM and titled “AHAM Performance Evaluation Procedure for Household Tumble Type Clothes Dryers”, June 1974, and designated as HLD–1.

1.8  “HLD–2EC” means the test standard promulgated by AHAM and titled “Test Method for Measuring Energy Consumption of Household Tumble Type Clothes Dryers,” December 1975, and designated as HLD–2EC.

1.9  “Standard size” means a clothes dryer with a drum capacity of 4.4 cubic feet or greater.

1.10  “Moisture content” means the ratio of the weight of water contained by the test load to the bone-dry weight of the test load, expressed as a percent.

1.11  “Automatic termination control” means a dryer control system with a sensor which monitors either the dryer load temperature or its moisture content and with a controller which automatically terminates the drying process. A mark or detent which indicates a preferred automatic termination control setting must be present if the dryer is to be classified as having an “automatic termination control.” A mark is a visible single control setting on one or more dryer controls.

1.12  “Temperature sensing control” means a system which monitors dryer exhaust air temperature and automatically terminates the dryer cycle.

1.13  “Moisture sensing control” means a system which utilizes a moisture sensing element within the dryer drum that monitors the amount of moisture in the clothes and automatically terminates the dryer cycle.

2. Testing Conditions

2.1  Installation. Install the clothes dryer in accordance with manufacturer's instructions. The dryer exhaust shall be restricted by adding the AHAM exhaust simulator described in 3.3.5 of HLD–1. All external joints should be taped to avoid air leakage. Disconnect all console light or other lighting systems on the clothes dryer which do not consume more than 10 watts during the clothes dryer test cycle.

2.2  Ambient temperature and humidity. Maintain the room ambient air temperature at 75 ±3 °F and the room relative humidity at 50±10 percent relative humidity.

2.3  Energy supply.

2.3.1  Electrical supply. Maintain the electrical supply at the clothes dryer terminal block within 1 percent of 120/240 or 120/208Y or 120 volts as applicable to the particular terminal block wiring system and within 1 percent of the nameplate frequency as specified by the manufacturer. If the dryer has a dual voltage conversion capability, conduct test at the highest voltage specified by the manufacturer.

2.3.2  Gas supply.

2.3.2.1  Natural gas. Maintains the gas supply to the clothes dryer at a normal inlet test pressure immediately ahead of all controls at 7 to 10 inches of water column. If the clothes dryer is equipped with a gas appliance pressure regulator, the regulator outlet pressure at the normal test pressure shall be approximately that recommended by the manufacturer. The hourly Btu rating of the burner shall be maintained within ±5 percent of the rating specified by the manufacturer. The natural gas supplied should have a heating value of approximately 1,025 Btu's per standard cubic foot. The actual heating value, H_n2, in Btu's per standard cubic foot, for the natural gas to be used in the test shall be obtained either from measurements made by the manufacturer conducting the test using a standard continuous flow calorimeter as described in 2.4.6 or by the purchase of bottled natural gas whose Btu rating is certified to be at least as accurate a rating as could be obtained from measurements with a standard continuous flow calorimeter as described in 2.4.6.

2.3.2.2  Propane gas. Maintain the gas supply to the clothes dryer at a normal inlet test pressure immediately ahead of all controls at 11 to 13 inches of water column. If the clothes dryer is equipped with a gas appliance pressure regulator, the regulator outlet pressure at the normal test pressure shall be approximately that recommended by the manufacturer. The hourly Btu rating of the burner shall be maintained within ±5 percent of the rating specified by the manufacturer. The propane gas supplied should have a heating value of approximately 2,500 Btu's per standard cubic foot. The actual heating value, H_p, in Btu's per standard cubic foot, for the propane gas to be used in the test shall be obtained either from measurements made by the manufacturer conducting the test using a standard continuous flow calorimeter as described in 2.4.6 or by the purchase of bottled gas whose Btu rating is certified to be at least as accurate a rating as could be obtained from measurement with a standard continuous calorimeter as described in 2.4.6.

2.4  Instrumentation. Perform all test measurements using the following instruments as appropriate.

2.4.1  Weighing scale for test cloth. The scale shall have a range of 0 to a maximum of 30 pounds with a resolution of at least 0.2 ounces and a maximum error no greater than 0.3 percent of any measured value within the range of 3 to 15 pounds.

2.4.1.2  Weighing scale for drum capacity measurements. The scale should have a range of 0 to a maximum of 500 pounds with resolution of 0.50 pounds and a maximum error no greater than 0.5 percent of the measured value.

2.4.2  Kilowatt-hour meter. The kilowatt-hour meter shall have a resolution of 0.001 kilowatt-hours and a maximum error no greater than 0.5 percent of the measured value.

2.4.3  Gas meter. The gas meter shall have a resolution of 0.001 cubic feet and a maximum error no greater than 0.5 percent of the measured value.

2.4.4  Dry and wet bulb psychrometer. The dry and wet bulb psychrometer shall have an error no greater than ±1 °F.

2.4.5  Temperature. The temperature sensor shall have an error no greater than ±1 °F.

2.4.6  Standard Continuous Flow Calorimeter. The Calorimeter shall have an operating range of 750 to 3,500 Btu per cubic feet. The maximum error of the basic calorimeter shall be no greater than 0.2 percent of the actual heating value of the gas used in the test. The indicator readout shall have a maximum error no greater than 0.5 percent of the measured value within the operating range and a resolution of 0.2 percent of the full scale reading of the indicator instrument.

2.5  Lint trap. Clean the lint trap thoroughly before each test run.

2.6  Test cloths.

2.6.1  Energy test cloth. The energy test cloth shall be clean and consist of the following:

(a) Pure finished bleached cloth, made with a momie or granite weave, which is a blended fabric of 50 percent cotton and 50 percent polyester and weighs within +10 percent of 5.75 ounces per square yard after test cloth preconditioning and has 65 ends on the warp and 57 picks on the fill. The individual warp and fill yarns are a blend of 50 percent cotton and 50 percent polyester fibers.

(b) Cloth material that is 24 inches by 36 inches and has been hemmed to 22 inches by 34 inches before washing. The maximum shrinkage after five washes shall not be more than four percent on the length and width.

(c) The number of test runs on the same energy test cloth shall not exceed 25 runs.

2.6.2  Energy stuffer cloths. The energy stuffer cloths shall be made from energy test cloth material and shall consist of pieces of material that are 12 inches by 12 inches and have been hemmed to 10 inches by 10 inches before washing. The maximum shrinkage after five washes shall not be more than four percent on the length and width. The number of test runs on the same energy stuffer cloth shall not exceed 25 runs after test cloth preconditioning.

2.6.3  Test Cloth Preconditioning.

A new test cloth load and energy stuffer cloths shall be treated as follows:

(1) Bone dry the load to a weight change of ±1 percent, or less, as prescribed in Section 1.2.

(2) Place test cloth load in a standard clothes washer set at the maximum water fill level. Wash the load for 10 minutes in soft water (17 parts per million hardness or less), using 6.0 grams of AHAM Standard Test Detergent, IIA, per gallon of water. Wash water temperature is to controlled at 140°±5 °F (60°±2.7 °C). Rinse water temperature is to be controlled at 100°±5 °F (37.7±2.7 °C).

(3) Rinse the load again at the same water temperature.

(4) Bone dry the load as prescribed in Section 1.2 and weigh the load.

(5) This procedure is repeated until there is a weight change of one percent or less.

(6) A final cycle is to be a hot water wash with no detergent, followed by two warm water rinses.

2.7  Test loads.

2.7.1  Compact size dryer load. Prepare a bone-dry test load of energy cloths which weighs 3.00 pounds ±.03 pounds. Adjustments to the test load to achieve the proper weight can be made by the use of energy stuffer cloths, with no more than five stuffer cloths per load. Dampen the load by agitating it in water whose temperature is 100° ±5 °F and consists of 0 to 17 parts per million hardness for approximately two minutes in order to saturate the fabric. Then, extract water from the wet test load by spinning the load until the moisture content of the load is between 66.5 percent to 73.5 percent of the bone-dry weight of the test load.

2.7.2  Standard size dryer load. Prepare a bone-dry test load of energy cloths which weighs 7.00 pounds ±.07 pounds. Adjustments to the test load to achieve the proper weight can be made by the use of energy stuffer cloths, with no more than five stuffer cloths per load. Dampen the load by agitating it in water whose temperature is 100° ±5 °F and consists of 0 to 17 parts per million hardness for approximately two minutes in order to saturate the fabric. Then, extract water from the wet test load by spinning the load until the moisture content of the load is between 66.5 percent to 73.5 percent of the bone-dry weight of the test load.

2.7.3  Method of loading. Load the energy test cloths by grasping them in the center, shaking them to hang loosely and then dropping them in the dryer at random.

2.8  Clothes dryer preconditioning. Before any test cycle, operate the dryer without a test load in the non-heat mode for 15 minutes or until the discharge air temperature is varying less than 1 °F for 10 minutes, which ever is longer, in the test installation location with the ambient conditions within the specified rest condition tolerances of 2.2.

3. Test Procedures and Measurements

3.1  Drum capacity. Measure the drum capacity by sealing all openings in the drum except the loading port with a plastic bag, and ensure that all corners and depressions are filled and that there are no extrusions of the plastic bag through the opening in the drum. Support the dryer's rear drum surface on a platform scale to prevent deflection of the dryer, and record the weight of the empty dryer. Fill the drum with water to a level determined by the intersection of the door plane and the loading port. Record the temperature of the water and then the weight of the dryer with the added water and then determine the mass of the water in pounds. Add or subtract the appropriate volume depending on whether or not the plastic bag protrudes into the drum interior. The drum capacity is calculated as follows:

C=w/d

C= capacity in cubic feet.

w= weight of water in pounds.

d= density of water at the measured temperature in pounds per cubic feet.

3.2  Dryer loading. Load the dryer as specified in 2.7.

3.3  Test cycle. Operate the clothes dryer at the maximum temperature setting and, if equipped with a timer, at the maximum time setting and dry the test load until the moisture content of the test load is between 2.5 percent to 5.0 percent of the bone-dry weight of the test load, but do not permit the dryer to advance into cool down. If required, reset the timer or automatic dry control.

3.4  Data recording. Record for each test cycle:

3.4.1  Bone-dry weight of the test load described in 2.7.

3.4.2  Moisture content of the wet test load before the test, as described in 2.7.

3.4.3  Moisture content of the dry test load obtained after the test described in 3.3.

3.4.4  Test room conditions, temperature and percent relative humidity described in 2.2.

3.4.5  For electric dryers—the total kilowatt-hours of electric energy, E_t, consumed during the test described in 3.3.

3.4.6  For gas dryers:

3.4.6.1  Total kilowatt-hours of electrical energy, E_te, consumed during the test described in 3.3.

3.4.6.2  Cubic feet of gas per cycle, E_tg, consumed during the test described in 3.3.

3.4.6.3  On gas dryers using a continuously burning pilot light—the cubic feet of gas, E_pg, consumed by the gas pilot light in one hour.

3.4.6.4  Correct the gas heating value, GEF, as measured in 2.3.2.1 and 2.3.2.2, to standard pressure and temperature conditions in accordance with U.S. Bureau of Standards, circular C417, 1938. A sample calculation is illustrated in Appendix E of HLD–1.

3.5  Test for automatic termination field use factor credits. Credit for automatic termination can be claimed for those dryers which meet the requirements for either temperature-sensing control, 1.12, or moisture sensing control, 1.13, and having present the appropriate mark or detent feed defined in 1.11.

4. Calculation of Derived Results From Test Measurements

4.1  Total per-cycle electric dryer energy consumption. Calculate the total electric dryer energy consumption per cycle, E_ce expressed in kilowatt-hours per cycle and defined as:

E_ce=[66/Ww−Wd)]×Ett×FU

Et=the energy recorded in 3.4.5.

66=an experimentally established value for the percent reduction in the moisture content of the test load during a laboratory test cycle expressed as a percent.

FU=Field use factor.

  =1.18 for time termination control systems.

  =1.04 for automatic control systems which meet the requirements of the definitions for automatic termination controls in 1.11.1, 1.12 and 1.13.

W_w=the moisture content of the wet test load as recorded in 3.4.2.

W_d=the moisture content of the dry test load as recorded in 3.4.3.

4.2  Per-cycle gas dryer electrical energy consumption. Calculate the gas dryer electrical energy consumption per cycle, E_ge, expressed in kilowatt-hours per cycle and defined as:

Ege=[66/(Ww−Wd)]×Ete×FU

Ete=the energy recorded in 3.4.6.1

FU, 66, Ww, Wd as defined in 4.1

4.3  Per-cycle gas dryer gas energy consumption. Calculate the gas dryer gas energy consumption per cycle, Ege. expressed in Btu's per cycle as defined as:

Egg=[66/(Ww−Wd)]×Etg×FU×GEF

Etg=the energy recorded in 3.4.6.2

GEF=corrected gas heat value (Btu per cubic feet) as defined in 3.4.6.4

FU, 66, Ww Wd as defined in 4.1

4.4  Per-cycle gas dryer continuously burning pilot light gas energy consumption. Calculate the gas dryer continuously burning pilot light gas energy consumption per cycle, Eup expressed in Btu's per cycle and defined as:

Eup=Epg×(8760−140/416)×GEF

Epg=the energy recorded in 3.4.6.3

8760=number of hours in a year

416=representative average number of clothes dryer cycles in a year

140=estimated number of hours that the continuously burning pilot light is on during the operation of the clothes dryer for the representative average use cycle for clothes dryers (416 cycles per year)

GEF as defined in 4.3

4.5  Total per-cycle gas dryer gas energy consumption expressed in Btu's. Calculate the total gas dryer energy consumption per cycle, Eg, expressed in Btu's per cycle and defined as:

Eg=Egg+Eup

Egg as defined in 4.3

Eup as defined in 4.4

4.6  Total per-cycle gas dryer energy consumption expressed in kilowatt-hours. Calculate the total gas dryer energy consumption per cycle, Ecg, expressed in kilowatt-hours per cycle and defined as:

Ecg=Ege+(Eg/3412 Btu/k Wh)

Ege as defined in 4.2

Eg as defined in 4.5

[46 FR 27326, May 19, 1981]

1. Definitions

1.1  Cut-in means the time when or water temperature at which a water heater control or thermostat acts to increase the energy or fuel input to the heating elements, compressor, or burner.

1.2  Cut-out means the time when or water temperature at which a water heater control or thermostat acts to reduce to a minimum the energy or fuel input to the heating elements, compressor, or burner.

1.3  Design Power Rating means the nominal power rating that a water heater manufacturer assigns to a particular design of water heater, expressed in kilowatts or Btu (kJ) per hour as appropriate.

1.4  Energy Factor means a measure of water heater overall efficiency.

1.5  First-Hour Rating means an estimate of the maximum volume of “hot” water that a storage-type water heater can supply within an hour that begins with the water heater fully heated (i.e., with all thermostats satisfied). It is a function of both the storage volume and the recovery rate.

1.6  Heat Trap means a device which can be integrally connected or independently attached to the hot and/or cold water pipe connections of a water heater such that the device will develop a thermal or mechanical seal to minimize the recirculation of water due to thermal convection between the water heater tank and its connecting pipes.

1.7  Instantaneous Water Heaters

1.7.1  Electric Instantaneous Water Heater Reserved.

1.7.2  Gas Instantaneous Water Heater means a water heater that uses gas as the energy source, initiates heating based on sensing water flow, is designed to deliver water at a controlled temperature of less than 180 °F (82 °C), has an input greater than 50,000 Btu/h (53 MJ/h) but less than 200,000 Btu/h (210 MJ/h), and has a manufacturer's specified storage capacity of less than 2 gallons (7.6 liters). The unit may use a fixed or variable burner input.

1.8  Maximum gpm (L/min) Rating means the maximum gallons per minute (liters per minute) of hot water that can be supplied by an instantaneous water heater while maintaining a nominal temperature rise of 77 °F (42.8 °C) during steady state operation.

1.9  Rated Storage Volume means the water storage capacity of a water heater, in gallons (liters), as specified by the manufacturer.

1.10  Recovery Efficiency means the ratio of energy delivered to the water to the energy content of the fuel consumed by the water heater.

1.11  Standby means the time during which water is not being withdrawn from the water heater. There are two standby time intervals used within this test procedure: τ_stby,1 represents the elapsed time between the time at which the maximum mean tank temperature is observed after the sixth draw and subsequent recovery and the end of the 24-hour test; τ_stby,2 represents the total time during the 24-hour simulated use test when water is not being withdrawn from the water heater.

1.12  Storage-type Water Heaters

1.12.1  Electric Storage-type Water Heater means a water heater that uses electricity as the energy source, is designed to heat and store water at a thermostatically controlled temperature of less than 180 °F (82 °C), has a nominal input of 12 kilowatts (40,956 Btu/h) or less, and has a rated storage capacity of not less than 20 gallons (76 liters) nor more than 120 gallons (450 liters).

1.12.2  Gas Storage-type Water Heater means a water heater that uses gas as the energy source, is designed to heat and store water at a thermostatically controlled temperature of less than 180 °F (82 °C), has a nominal input of 75,000 Btu (79 MJ) per hour or less, and has a rated storage capacity of not less than 20 gallons (76 liters) nor more than 100 gallons (380 liters).

1.12.3  Heat Pump Water Heater means a water heater that uses electricity as the energy source, is designed to heat and store water at a thermostatically controlled temperature of less than 180 °F (82 °C), has a maximum current rating of 24 amperes (including the compressor and all auxiliary equipment such as fans, pumps, controls, and, if on the same circuit, any resistive elements) for an input voltage of 250 volts or less, and, if the tank is supplied, has a manufacturer's rated storage capacity of 120 gallons (450 liters) or less. Resistive elements used to provide supplemental heating may use the same circuit as the compressor if (1) an interlocking mechanism prevents concurrent compressor operation and resistive heating or (2) concurrent operation does not result in the maximum current rating of 24 amperes being exceeded. Otherwise, the resistive elements and the heat pump components must use separate circuits. A heat pump water heater may be sold by the manufacturer with or without a storage tank.

a. Heat Pump Water Heater with Storage Tank means an air-to-water heat pump sold by the manufacturer with an insulated storage tank as a packaged unit. The tank and heat pump can be an integral unit or they can be separated.

b. Heat Pump Water Heater without Storage Tank (also called Add-on Heat Pump Water Heater) means an air-to-water heat pump designed for use with a storage-type water heater or a storage tank that is not specified or supplied by the manufacturer.

1.12.4  Oil Storage-type Water Heater means a water heater that uses oil as the energy source, is designed to heat and store water at a thermostatically controlled temperature of less than 180 °F (82 °C), has a nominal energy input of 105,000 Btu/h (110 MJ/h) or less, and has a manufacturer's rated storage capacity of 50 gallons (190 liters) or less.

1.12.5  Storage-type Water Heater of More than 2 Gallons (7.6 Liters) and Less than 20 Gallons (76 Liters). Reserved.

1.13  ASHRAE Standard 41.1–86 means the standard published in 1986 by the American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc., and titled Standard Measurement Guide: Section on Temperature Measurements.

1.14  ASTM–D–2156–80 means the test standard published in 1980 by the American Society for Testing and Measurements and titled “Smoke Density in Flue Gases from Burning Distillate Fuels, Test Method for”.

1.15  Symbol Usage The following identity relationships are provided to help clarify the symbology used throughout this procedure:

C_p specific heat capacity of water

E_annual annual energy consumption of a water heater

E_f energy factor of a water heater

F_hr first-hour rating of a storage-type water heater

F_max maximum gpm (L/min) rating of an instantaneous water heater rated at a temperature rise of 77 °F (42.8 °C) across the heater

i a subscript to indicate an ith draw during a test

M_i mass of water removed during the ith draw (i=1 to 6) of the 24-hr simulated use test

M*_i for storage-type water heaters, mass of water removed during the ith draw (i=1 to n) during the first-hour rating test

M_10m for instantaneous water heaters, mass of water removed continuously during a 10-minute interval in the maximum gpm (L/min) rating test

n for storage-type water heaters, total number of draws during the first-hour rating test

Q total fossil fuel and/or electric energy consumed during the entire 24-hr simulated use test

Q_d daily water heating energy consumption adjusted for net change in internal energy

Q_da adjusted daily water heating energy consumption with adjustment for variation of tank to ambient air temperature difference from nominal value

Q_dm overall adjusted daily water heating energy consumption including Q_da and Q_HWD

Q_hr hourly standby losses

Q_HW daily energy consumption to heat water over the measured average temperature rise across the water heater

Q_HWD adjustment to daily energy consumption, Q_hw, due to variation of the temperature rise across the water heater not equal to the nominal value of 77 °F (42.8 °C)

Q_r energy consumption of fossil fuel or heat pump water heaters between thermostat (or burner) cut-out prior to the first draw and cut-out following the first draw of the 24-hr simulated use test

Q_{r, max} energy consumption of a modulating instantaneous water heater between cut-out (burner) prior to the first draw and cut-out following the first draw of the 24-hr simulated use test

Q_{r, min} energy consumption of a modulating instantaneous water heater from immediately prior to the fourth draw to burner cut-out following the fourth draw of the 24-hr simulated use test

Q_stby total energy consumed by the water heater during the standby time interval τ_{stby, 1}

Q_su total fossil fueled and/or electric energy consumed from the beginning of the first draw to the thermostat (or burner) cut-out following the completion of the sixth draw during the 24-hr simulated use test

T_min for modulating instantaneous water heaters, steady state outlet water temperature at the minimum fuel input rate

T ₀ mean tank temperature at the beginning of the 24-hr simulated use test

T ₂₄ mean tank temperature at the end of the 24-hr simulated use test

T _{a, stby} average ambient air temperature during standby periods of the 24-hr use test

T _del for instantaneous water heaters, average outlet water temperature during a 10-minute continuous draw interval in the maximum gpm (L/min) rating test

T _{del, i} average outlet water temperature during the ith draw of the 24-hr simulated use test

T _in for instantaneous water heaters, average inlet water temperature during a 10-minute continuous draw interval in the maximum gpm (L/min) rating test

T _{in, i} average inlet water temperature during the ith draw of the 24-hr simulated use test

T _{max, 1} maximum measured mean tank temperature after cut-out following the first draw of the 24-hr simulated use test

T _stby average storage tank temperature during the standby period τ_{stby, 2} of the 24-hr use test

T _su maximum measured mean tank temperature after cut-out following the sixth draw of the 24-hr simulated use test

T _{t, stby} average storage tank temperature during the standby period τ_stby, 1 of the 24-hr use test

T *_{del, i} for storage-type water heaters, average outlet water temperature during the ith draw (i=1 to n) of the first-hour rating test

T*_{max, i} for storage-type water heaters, maximum outlet water temperature observed during the ith draw (i=1 to n) of the first-hour rating test

T*_{min, i} for storage-type water heaters, minimum outlet water temperature to terminate the ith draw during the first-hour rating test

UA standby loss coefficient of a storage-type water heater

V_i volume of water removed during the ith draw (i=1 to 6) of the 24-hr simulated use test

V*_i volume of water removed during the ith draw (i=1 to n) during the first-hour rating test

V_10m for instantaneous water heaters, volume of water removed continuously during a 10-minute interval in the maximum gpm (L/min) rating test

V_max steady state water flow rate of an instantaneous water heater at the rated input to give a discharge temperature of 135 °F ±5 °F (57.2 °C ±2.8 °C)

V_min steady state water flow rate of a modulating instantaneous water heater at the minimum input to give a discharge temperature of T_min up to 135 °F ±5 °F (57.2 °C ±2.8 °C)

V_st measured storage volume of the storage tank

W_f weight of storage tank when completely filled with water

W_t tare weight of storage tank when completely empty of water

ⁿ_r recovery efficiency

^p density of water

τ_{stby, 1} elapsed time between the time the maximum mean tank temperature is observed after the sixth draw and the end of the 24-hr simulated use test

τ_{stby, 2} overall standby periods when no water is withdrawn during the 24-hr simulated use test

1.16 Tabletop water heater means a water heater in a rectangular box enclosure designed to slide into a kitchen countertop space with typical dimensions of 36 inches high, 25 inches deep and 24 inches wide.

2. Test Conditions

2.1  Installation Requirements. Tests shall be performed with the water heater and instrumentation installed in accordance with Section 4 of this appendix.

2.2  Ambient Air Temperature. The ambient air temperature shall be maintained between 65.0 °F and 70.0 °F (18.3 °C and 21.1 °C) on a continuous basis. For heat pump water heaters, the dry bulb temperature shall be maintained at 67.5 °F ±1 °F (19.7 °C ±0.6 °C) and, in addition, the relative humidity shall be maintained between 49% and 51%.

2.3  Supply Water Temperature. The temperature of the water being supplied to the water heater shall be maintained at 58 °F ±2 °F (14.4 °C ±1.1 °C) throughout the test.

2.4  Storage Tank Temperature. The average temperature of the water within the storage tank shall be set to 135 °F ±5 °F (57.2 °C ±2.8 °C).

2.5  Supply Water Pressure. During the test when water is not being withdrawn, the supply pressure shall be maintained between 40 psig (275 kPa) and the maximum allowable pressure specified by the water heater manufacturer.

2.6  Electrical and/or Fossil Fuel Supply.

2.6.1  Electrical. Maintain the electrical supply voltage to within ±1% of the center of the voltage range specified by the water heater and/or heat pump manufacturer.

2.6.2  Natural Gas. Maintain the supply pressure in accordance with the manufacturer's specifications. If the supply pressure is not specified, maintain a supply pressure of 7–10 inches of water column (1.7–2.5 kPa). If the water heater is equipped with a gas appliance pressure regulator, the regulator outlet pressure shall be within ±10% of the manufacturer's specified manifold pressure. For all tests, use natural gas having a heating value of approximately 1,025 Btu per standard cubic foot (38,190 kJ per standard cubic meter).

2.6.3  Propane Gas. Maintain the supply pressure in accordance with the manufacturer's specifications. If the supply pressure is not specified, maintain a supply pressure of 11–13 inches of water column (2.7–3.2 kPa). If the water heater is equipped with a gas appliance pressure regulator, the regulator outlet pressure shall be within ±10% of the manufacturer's specified manifold pressure. For all tests, use propane gas with a heating value of approximately 2,500 Btu per standard cubic foot (93,147 kJ per standard cubic meter).

2.6.4  Fuel Oil Supply. Maintain an uninterrupted supply of fuel oil. Use fuel oil having a heating value of approximately 138,700 Btu per gallon (38,660 kJ per liter).

3. Instrumentation

3.1  Pressure Measurements. Pressure-measuring instruments shall have an error no greater than the following values:

3.2  Temperature Measurement

3.2.1  Measurement. Temperature measurements shall be made in accordance with the Standard Measurement Guide: Section on Temperature Measurements, ASHRAE Standard 41.1–86.

3.2.2  Accuracy and Precision. The accuracy and precision of the instruments, including their associated readout devices, shall be within the following limits:

3.2.3  Scale Division. In no case shall the smallest scale division of the instrument or instrument system exceed 2 times the specified precision.

3.2.4  Temperature Difference. Temperature difference between the entering and leaving water may be measured with any of the following:

a. A thermopile

b. Calibrated resistance thermometers

c. Precision thermometers

d. Calibrated thermistors

e. Calibrated thermocouples

f. Quartz thermometers

3.2.5  Thermopile Construction. If a thermopile is used, it shall be made from calibrated thermocouple wire taken from a single spool. Extension wires to the recording device shall also be made from that same spool.

3.2.6  Time Constant. The time constant of the instruments used to measure the inlet and outlet water temperatures shall be no greater than 5 seconds.

3.3  Liquid Flow Rate Measurement. The accuracy of the liquid flow rate measurement, using the calibration if furnished, shall be equal to or less than ±1% of the measured value in mass units per unit time.

3.4  Electric Energy. The electrical energy used shall be measured with an instrument and associated readout device that is accurate within ±1% of the reading.

3.5  Fossil Fuels. The quantity of fuel used by the water heater shall be measured with an instrument and associated readout device that is accurate within ±1% of the reading.

3.6  Mass Measurements. For mass measurements greater than or equal to 10 pounds (4.5 kg), a scale that is accurate within ±1% of the reading shall be used to make the measurement. For mass measurements less than 10 pounds (4.5 kg), the scale shall provide a measurement that is accurate within ±0.1 pound (0.045 kg).

3.7  Heating Value. The higher heating value of the natural gas, propane, or fuel oil shall be measured with an instrument and associated readout device that is accurate within ±1% of the reading. The heating value of natural gas and propane must be corrected for local temperature and pressure conditions.

3.8  Time. The elapsed time measurements shall be measured with an instrument that is accurate within ±0.5 seconds per hour.

3.9  Volume. Volume measurements shall be measured with an accuracy of ±2% of the total volume.

4. Installation

4.1  Water Heater Mounting. A water heater designed to be freestanding shall be placed on a 3/4 inch (2 cm) thick plywood platform supported by three 2 × 4 inch (5 cm × 10 cm) runners. If the water heater is not approved for installation on combustible flooring, suitable non-combustible material shall be placed between the water heater and the platform. Counter-top water heaters shall be placed against a simulated wall section. Wall-mounted water heaters shall be supported on a simulated wall in accordance with the manufacturer-published installation instructions. When a simulated wall is used, the recommended construction is 2 × 4 inch (5 cm × 10 cm) studs, faced with 3/4 inch (2 cm) plywood. For heat pump water heaters that are supplied with a storage tank, the two components, if not delivered as a single package, shall be connected in accordance with the manufacturer-published installation instructions and the overall system shall be placed on the above-described plywood platform. If installation instructions are not provided by the heat pump manufacturer, uninsulated 8 foot (2.4 m) long connecting hoses having an inside diameter of 5/8 inch (1.6 cm) shall be used to connect the storage tank and the heat pump water heater. With the exception of using the storage tank described in 4.10, the same requirements shall apply for heat pump water heaters that are supplied without a storage tank from the manufacturer. The testing of the water heater shall occur in an area that is protected from drafts.

4.2  Water Supply. Connect the water heater to a water supply capable of delivering water at conditions as specified in Sections 2.3 and 2.5 of this appendix.

4.3  Water Inlet and Outlet Configuration. For freestanding water heaters that are taller than 36 inches (91.4 cm), inlet and outlet piping connections shall be configured in a manner consistent with Figures 1 and 2. Inlet and outlet piping connections for wall-mounted water heaters shall be consistent with Figure 3. For freestanding water heaters that are 36 inches or less in height and not supplied as part of a counter-top enclosure (commonly referred to as an under-the-counter model), inlet and outlet piping shall be installed in a manner consistent with Figures 4, 5, and 6. For water heaters that are supplied with a counter-top enclosure, inlet and outlet piping shall be made in a manner consistent with Figures 7A and 7B, respectively. The vertical piping noted in Figures 7A and 7B shall be located (whether inside the enclosure or along the outside in a recessed channel) in accordance with the manufacturer-published installation instructions.

All dimensions noted in Figures 1 through 7 shall be achieved. All piping between the water heater and the inlet and outlet temperature sensors, noted as T_IN and T_OUT in the figures, shall be Type “L” hard copper having the same diameter as the connections on the water heater. Unions may be used to facilitate installation and removal of the piping arrangements. A pressure gauge and diaphragm expansion tank shall be installed in the supply water piping at a location upstream of the inlet temperature sensor. An appropriately rated pressure and temperature relief valve shall be installed on all water heaters at the port specified by the manufacturer. Discharge piping for the relief valve shall be non-metallic. If heat traps, piping insulation, or pressure relief valve insulation are supplied with the water heater, they shall be installed for testing. Except when using a simulated wall, clearance shall be provided such that none of the piping contacts other surfaces in the test room.

4.4  Fuel and/or Electrical Power and Energy Consumption. Install one or more instruments which measure, as appropriate, the quantity and rate of electrical energy and/or fossil fuel consumption in accordance with Section 3. For heat pump water heaters that use supplemental resistive heating, the electrical energy supplied to the resistive element(s) shall be metered separately from the electrical energy supplied to the entire appliance or to the remaining components (e.g., compressor, fans, pumps, controls).

4.5  Internal Storage Tank Temperature Measurements. Install six temperature measurement sensors inside the water heater tank with a vertical distance of at least 4 inches (100 mm) between successive sensors. A temperature sensor shall be positioned at the vertical midpoint of each of the six equal volume nodes within the tank. Nodes designate the equal volumes used to evenly partition the total volume of the tank. As much as is possible, the temperature sensor should be positioned away from any heating elements, anodic protective devices, tank walls, and flue pipe walls. If the tank cannot accommodate six temperature sensors and meet the installation requirements specified above, install the maximum number of sensors which comply with the installation requirements. The temperature sensors shall be installed either through (1) the anodic device opening; (2) the relief valve opening; or (3) the hot water outlet. If installed through the relief valve opening or the hot water outlet, a tee fitting or outlet piping, as applicable, shall be installed as close as possible to its original location. If the relief valve temperature sensor is relocated, and it no longer extends into the top of the tank, a substitute relief valve that has a sensing element that can reach into the tank shall be installed. If the hot water outlet includes a heat trap, the heat trap shall be installed on top of the tee fitting. Added fittings shall be covered with thermal insulation having an R value between 4 and 8 h÷ft^2÷ °F/Btu (0.7 and 1.4 m^2÷ °C/W).

4.6  Ambient Air Temperature Measurement. Install an ambient air temperature sensor at the vertical mid-point of the water heater and approximately 2 feet (610 mm) from the surface of the water heater. The sensor shall be shielded against radiation.

4.7  Inlet and Outlet Water Temperature Measurements. Install temperature sensors in the cold-water inlet pipe and hot-water outlet pipe as shown in Figures 1, 2, 3, 4, 5, 6, 7a and 7b, as applicable.

4.8  Flow Control. A valve shall be installed to provide flow as specified in sections 5.1.4.1 for storage tank water heaters and 5.2.1 for instantaneous water heaters.

4.9  Flue Requirements.

4.9.1  Gas-Fired Water Heaters. Establish a natural draft in the following manner. For gas-fired water heaters with a vertically discharging draft hood outlet, a 5-foot (1.5-meter) vertical vent pipe extension with a diameter equal to the largest flue collar size of the draft hood shall be connected to the draft hood outlet. For gas-fired water heaters with a horizontally discharging draft hood outlet, a 90-degree elbow with a diameter equal to the largest flue collar size of the draft hood shall be connected to the draft hood outlet. A 5-foot (1.5-meter) length of vent pipe shall be connected to the elbow and oriented to discharge vertically upward. Direct vent gas-fired water heaters shall be installed with venting equipment specified in the manufacturer's instructions using the minimum vertical and horizontal lengths of vent pipe recommended by the manufacturer.

4.9.2  Oil-Fired Water Heaters. Establish a draft at the flue collar at the value specified in the manufacturer's instructions. Establish the draft by using a sufficient length of vent pipe connected to the water heater flue outlet, and directed vertically upward. For an oil-fired water heater with a horizontally discharging draft hood outlet, a 90-degree elbow with a diameter equal to the largest flue collar size of the draft hood shall be connected to the draft hood outlet. A length of vent pipe sufficient to establish the draft shall be connected to the elbow fitting and oriented to discharge vertically upward. Direct-vent oil-fired water heaters should be installed with venting equipment as specified in the manufacturer's instructions, using the minimum vertical and horizontal lengths of vent pipe recommended by the manufacturer.

4.10  Heat Pump Water Heater Storage Tank. The tank to be used for testing a heat pump water heater without a tank supplied by the manufacturer (see Section 1.12.3b) shall be an electric storage-type water heater having a measured volume of 47.0 gallons ±1.0 gallon (178 liters ±3.8 liters); two 4.5 kW heating elements controlled in such a manner as to prevent both elements from operating simultaneously; and an energy factor greater than or equal to the minimum energy conservation standard (as determined in accordance with Section 6.1.7) and less than or equal to the sum of the minimum energy conservation standard and 0.02.

5. Test Procedures

5.1  Storage-type Water Heaters, Including Heat Pump Water Heaters.

5.1.1  Determination of Storage Tank Volume. Determine the storage capacity, V_st, of the water heater under test, in gallons (liters), by subtracting the tare weight—measured while the tank is empty—from the gross weight of the storage tank when completely filled with water (with all air eliminated and line pressure applied as described in section 2.5) and dividing the resulting net weight by the density of water at the measured temperature.

5.1.2  Setting the Thermostat.

5.1.2.1  Single Thermostat Tanks. Starting with a tank at the supply water temperature, initiate normal operation of the water heater. After cut-out, determine the mean tank temperature every minute until the maximum value is observed. Determine whether this maximum value for the mean tank temperature is within the range of 135 °F±5 °F (57.2 °C±2.8 °C). If not, turn off the water heater, adjust the thermostat, drain and refill the tank with supply water. Then, once again, initiate normal operation of the water heater, and determine the maximum mean tank temperature after cut-out. Repeat this sequence until the maximum mean tank temperature after cut-out is 135 °F±5 °F (57.2 °C±2.8 °C).

5.1.2.2  Tanks with Two or More Thermostats. Follow the same sequence as for a single thermostat tank, i.e. start at the supply water temperature, operate normally until cutout. Determine if the thermostat that controls the uppermost heating element yields a maximum water temperature of 135 °F±5 °F (57.2 °C±2.8 °C), as measured by the in-tank sensors that are positioned above the uppermost heating element. If the tank temperature at the thermostat is not within 135 °F±5 °F (57.2 °C±2.8 °C), turn off the water heater, adjust the thermostat, drain and refill the tank with supply water. The thermostat that controls the heating element positioned next highest in the tank shall then be set to yield a maximum water temperature of 135 °F±5 °F (57.2 °C±2.8 °C). This process shall be repeated until the thermostat controlling the lowest element is correctly adjusted. When adjusting the thermostat that controls the lowest element, the maximum mean tank temperature after cut-out, as determined using all the in-tank sensors, shall be 135 °F±5 °F (57.2 °C±2.8 °C). When adjusting all other thermostats, use only the in-tank temperature sensors positioned above the heating element in question to evaluate the maximum water temperature after cut-out.

For heat pump water heaters that control an auxiliary resistive element, the thermostat shall be set in accordance with the manufacturer's installation instructions.

5.1.3  Power Input Determination. For all water heaters except electric types having immersed heating elements, initiate normal operation and determine the power input, P, to the main burners (including pilot light power, if any) after 15 minutes of operation. If the water heater is equipped with a gas appliance pressure regulator, the regulator outlet pressure shall be set within ±10% of that recommended by the manufacturer. For oil-fired water heaters the fuel pump pressure shall be within ±10% of the manufacturer's specified pump pressure. All burners shall be adjusted to achieve an hourly Btu (kJ) rating that is within ±2% of the value specified by the manufacturer. For an oil-fired water heater, adjust the burner to give a CO₂ reading recommended by the manufacturer and an hourly Btu (kJ) rating that is within ±2% of that specified by the manufacturer. Smoke in the flue may not exceed No. 1 smoke as measured by the procedure in ASTM–D–2156–80.

5.1.4  First-Hour Rating Test.

5.1.4.1  General. During hot water draws, remove water at a rate of 3.0±0.25 gallons per minute (11.4±0.95 liters per minute). Collect the water in a container that is large enough to hold the volume removed during an individual draw and suitable for weighing at the termination of each draw. Alternatively, a water meter may be used to directly measure the water volume(s) withdrawn.

5.1.4.2  Draw Initiation Criteria. Begin the first-hour rating test by imposing a draw on the storage-type water heater. After completion of this first draw, initiate successive draws based on the following criteria. For gas-and oil-fired water heaters, initiate successive draws when the thermostat acts to reduce the supply of fuel to the main burner. For electric water heaters having a single element or multiple elements that all operate simultaneously, initiate successive draws when the thermostat acts to reduce the electrical input supplied to the element(s). For electric water heaters having two or more elements that do not operate simultaneously, initiate successive draws when the applicable thermostat acts to reduce the electrical input to the element located vertically highest in the storage tank. For heat pump waters heaters that do not use supplemental resistive heating, initiate successive draws immediately after the electrical input to the compressor is reduced by the action of the water heater's thermostat. For heat pump waters heaters that use supplemental resistive heating, initiate successive draws immediately after the electrical input to the compressor or the uppermost resistive element is reduced by the action of the applicable water heater thermostat. This draw initiation criterion for heat pump water heaters that use supplemental resistive heating, however, shall only apply when the water located above the thermostat at cut-out is heated to 135 °F±5 °F (57.2 °C±2.8 °C).

5.1.4.3  Test Sequence. Establish normal water heater operation. If the water heater is not presently operating, initiate a draw. The draw may be terminated anytime after cut-in occurs. After cut-out occurs (i.e., all thermostats are satisfied), monitor the internal storage tank temperature sensors described in section 4.5 every minute.

Initiate a draw after a maximum mean tank temperature has been observed following cut-out. Record the time when the draw is initiated and designate it as an elapsed time of zero (τ* = 0). (The superscript * is used to denote variables pertaining to the first-hour rating test.) Record the outlet water temperature beginning 15 seconds after the draw is initiated and at 5-second intervals thereafter until the draw is terminated. Determine the maximum outlet temperature that occurs during this first draw and record it as T*_{max, 1}. For the duration of this first draw and all successive draws, in addition, monitor the inlet temperature to the water heater to ensure that the required 58 °F±2 °F (14.4 °C±1.1 °C) test condition is met. Terminate the hot water draw when the outlet temperature decreases to T*_max,1−25 °F (T*_max,1−13.9 °C). Record this temperature as T*_min,1. Following draw termination, determine the average outlet water temperature and the mass or volume removed during this first draw and record them as T *_del,1 and M*₁ or V*₁, respectively.

Initiate a second and, if applicable, successive draw each time the applicable draw initiation criteria described in section 5.1.4.2 are satisfied. As required for the first draw, record the outlet water temperature 15 seconds after initiating each draw and at 5-second intervals thereafter until the draw is terminated. Determine the maximum outlet temperature that occurs during each draw and record it as T*_{max, i}, where the subscript i refers to the draw number. Terminate each hot water draw when the outlet temperature decreases to T*_{max, i}−25 °F (T*_{max, i}−13.9 °C). Record this temperature as T*_{min, i}. Calculate and record the average outlet temperature and the mass or volume removed during each draw (T *_{del, i} and M*_i or V*_i, respectively). Continue this sequence of draw and recovery until one hour has elapsed, then shut off the electrical power and/or fuel supplied to the water heater.

If a draw is occurring at an elapsed time of one hour, continue this draw until the outlet temperature decreases to T*_{max, n}−25 °F (T*_{max, n} −13.9 °C), at which time the draw shall be immediately terminated. (The subscript n shall be used to denote quantities associated with the final draw.) If a draw is not occurring at an elapsed time of one hour, a final draw shall be imposed at one hour. This draw shall be immediately terminated when the outlet temperature first indicates a value less than or equal to the cut-off temperature used for the previous draw (T*_{min, n}−1). For cases where the outlet temperature is close to T*_{min, n}−1, the final draw shall proceed for a minimum of 30 seconds. If an outlet temperature greater than T*_{min, n}−1 is not measured within 30 seconds, the draw shall be immediately terminated and zero additional credit shall be given towards first-hour rating (i.e., M*_n = 0 or V*_n = 0). After the final draw is terminated, calculate and record the average outlet temperature and the mass or volume removed during the draw (T *_{del, n} and M*_n or V*_n, respectively).

5.1.5  24-Hour Simulated Use Test. During the simulated use test, a total of 64.±3 1.0 gallons (243±3.8 liters) shall be removed. This value is referred to as the daily hot water usage in the following text.

With the water heater turned off, fill the water heater with supply water and apply pressure as described in section 2.5. Turn on the water heater and associated heat pump unit, if present. After the cut-out occurs, the water heater may be operated for up to three cycles of drawing until cut-in, and then operating until cut-out, prior to the start of the test.

At this time, record the mean tank temperature (T _o), and the electrical and/or fuel measurement readings, as appropriate. Begin the 24-hour simulated use test by withdrawing a volume from the water heater that equals one-sixth of the daily hot water usage. Record the time when this first draw is initiated and assign it as the test elapsed time (τ) of zero (0). Record the average storage tank and ambient temperature every 15 minutes throughout the 24-hour simulated use test unless a recovery or a draw is occurring. At elapsed time intervals of one, two, three, four, and five hours from τ = 0, initiate additional draws, removing an amount of water equivalent to one-sixth of the daily hot water usage with the maximum allowable deviation for any single draw being ±0.5 gallons (1.9 liters). The quantity of water withdrawn during the sixth draw shall be increased or decreased as necessary such that the total volume of water withdrawn equals 64.3 gallons ±1.0 gallon (243.4 liters ±3.8 liters).

All draws during the simulated use test shall be made at flow rates of 3.0 gallons ±0.25 gallons per minute (11.4 liters ±0.95 liters per minute). Measurements of the inlet and outlet temperatures shall be made 15 seconds after the draw is initiated and at every subsequent 5-second interval throughout the duration of each draw. The arithmetic mean of the hot water discharge temperature and the cold water inlet temperature shall be determined for each draw (T _{del, i} and T _{in, i}). Determine and record the net mass or volume removed (M_i or V_i), as appropriate, after each draw.

At the end of the recovery period following the first draw, record the maximum mean tank temperature observed after cut-out, T _{max, 1}, and the energy consumed by an electric resistance, gas or oil-fired water heater, Q_r. For heat pump water heaters, the total electrical energy consumed during the first recovery by the heat pump (including compressor, fan, controls, pump, etc.) and, if applicable, by the resistive element(s) shall be recorded as Q_r.

At the end of the recovery period that follows the sixth draw, determine and record the total electrical energy and/or fossil fuel consumed since the beginning of the test, Q_su. In preparation for determining the energy consumed during standby, record the reading given on the electrical energy (watt-hour) meter, the gas meter, and/or the scale used to determine oil consumption, as appropriate. Record the maximum value of the mean tank temperature after cut-out as T _su. Except as noted below, allow the water heater to remain in the standby mode until 24 hours have elapsed from the start of the test (i.e., since = 0). Prevent the water heater from beginning a recovery cycle during the last hour of the test by turning off the electric power to the electrical heating elements and heat pump, if present, or by turning down the fuel supply to the main burner at an elapsed time of 23 hours. If a recovery is taking place at an elapsed time of 23 hours, wait until the recovery is complete before reducing the electrical and/or fuel supply to the water heater. At 24 hours, record the mean tank temperature, T ₂₄, and the electric and/or fuel instrument readings. Determine the total fossil fuel or electrical energy consumption, as appropriate, for the entire 24-hour simulated use test, Q. Record the time interval between the time at which the maximum mean tank temperature is observed after the sixth draw and the end of the 24-hour test as _{stby, 1}. Record the time during which water is not being withdrawn from the water heater during the entire 24-hour period as _{stby, 2}.

5.2  Instantaneous Gas and Electric Water Heaters

5.2.1  Setting the Outlet Discharge Temperature. Initiate normal operation of the water heater at the full input rating for electric instantaneous water heaters and at the maximum firing rate specified by the manufacturer for gas instantaneous water heaters. Monitor the discharge water temperature and set to a value of 135 °F ±5 °F (57.2 °C ±2.8 °C) in accordance with the manufacturer's instructions. If the water heater is not capable of providing this discharge temperature when the flow rate is 3.0 gallons ±0.25 gallons per minute (11.4 liters ±0.95 liters per minute), then adjust the flow rate as necessary to achieve the specified discharge water temperature. Record the corresponding flow rate as V_max.

5.2.2  Additional Requirements for Variable Input Instantaneous Gas Water Heaters. If the instantaneous water heater incorporates a controller that permits operation at a reduced input rate, adjust the flow rate as necessary to achieve a discharge water temperature of 135 °F ±5 °F (57.2 °C ±2.8 °C) while maintaining the minimum input rate. Record the corresponding flow rate as V_min. If an outlet temperature of 135 °F ±5 °F (57.2 °C ±2.8 °C) cannot be achieved at the minimum flow rate permitted by the instantaneous water heater, record the flow rate as V_min and the corresponding outlet temperature as T_min.

5.2.3  Maximum GPM Rating Test for Instantaneous Water Heaters. Establish normal water heater operation at the full input rate for electric instantaneous water heaters and at the maximum firing rate for gas instantaneous water heaters with the discharge water temperature set in accordance with Section 5.2.1. During the 10-minute test, either collect the withdrawn water for later measurement of the total mass removed, or alternatively, use a water meter to directly measure the water volume removed.

After recording the scale or water meter reading, initiate water flow throughout the water heater, record the inlet and outlet water temperatures beginning 15 seconds after the start of the test and at subsequent 5-second intervals throughout the duration of the test. At the end of 10 minutes, turn off the water. Determine the mass of water collected, M_10m, in pounds (kilograms), or the volume of water, V_10m, in gallons (liters).

5.2.4 24-hour Simulated Use Test for Gas Instantaneous Water Heaters.

5.2.4.1  Fixed Input Instantaneous Water Heaters. Establish normal operation with the discharge water temperature and flow rate set to values of 135 °F ±5 °F (57.2 °C ±2.8 °C) and V_max per Section 5.2.1, respectively. With no draw occurring, record the reading given by the gas meter and/or the electrical energy meter as appropriate. Begin the 24-hour simulated use test by drawing an amount of water out of the water heater equivalent to one-sixth of the daily hot water usage. Record the time when this first draw is initiated and designate it as an elapsed time, τ, of 0. At elapsed time intervals of one, two, three, four, and five hours from τ = 0, initiate additional draws, removing an amount of water equivalent to one-sixth of the daily hot water usage, with the maximum allowable deviation for any single draw being ±0.5 gallons (1.9 liters). The quantity of water drawn during the sixth draw shall be increased or decreased as necessary such that the total volume of water withdrawn equals 64.3 gallons ±1.0 gallons (243.4 liters ±3.8 liters).

Measurements of the inlet and outlet water temperatures shall be made 15 seconds after the draw is initiated and at every 5-second interval thereafter throughout the duration of the draw. The arithmetic mean of the hot water discharge temperature and the cold water inlet temperature shall be determined for each draw. Record the scale used to measure the mass of the withdrawn water or the water meter reading, as appropriate, after each draw. At the end of the recovery period following the first draw, determine and record the fossil fuel or electrical energy consumed, Q_r. Following the sixth draw and subsequent recovery, allow the water heater to remain in the standby mode until exactly 24 hours have elapsed since the start of the test (i.e., since τ = 0). At 24 hours, record the reading given by the gas meter and/or the electrical energy meter as appropriate. Determine the fossil fuel or electrical energy consumed during the entire 24-hour simulated use test and designate the quantity as Q.

5.2.4.2  Variable Input Instantaneous Water Heaters. If the instantaneous water heater incorporates a controller that permits continuous operation at a reduced input rate, the first three draws shall be conducted using the maximum flow rate, V_max, while removing an amount of water equivalent to one-sixth of the daily hot water usage, with the maximum allowable deviation for any one of the three draws being ±0.5 gallons (1.9 liters). The second three draws shall be conducted at V_min. If an outlet temperature of 135 °F ±5 °F (57.2 °C ±2.8 °C) could not be achieved at the minimum flow rate permitted by the instantaneous water heater, the last three draws should be lengthened such that the volume removed is:

or

where T_min is the outlet water temperature at the flow rate V_min as determined in Section 5.2.1, and where the maximum allowable variation for any one of the three draws is ±0.5 gallons (1.9 liters). The quantity of water withdrawn during the sixth draw shall be increased or decreased as necessary such that the total volume of water withdrawn equals (32.15 + 3_÷V_4,5,6) ±1.0 gallons

((121.7 + 3 ÷ V_4,5,6) ±3.8 liters).

Measurements of the inlet and outlet water temperatures shall be made 5 seconds after a draw is initiated and at every 5-second interval thereafter throughout the duration of the draw. Determine the arithmetic mean of the hot water discharge temperature and the cold water inlet temperature for each draw. Record the scale used to measure the mass of the withdrawn water or the water meter reading, as appropriate, after each draw. At the end of the recovery period following the first draw, determine and record the fossil fuel or electrical energy consumed, Q_{r, max}. Likewise, record the reading of the meter used to measure fossil fuel or electrical energy consumption prior to the fourth draw and at the end of the recovery period following the fourth draw, and designate the difference as Q_r,min. Following the sixth draw and subsequent recovery, allow the water heater to remain in the standby mode until exactly 24 hours have elapsed since the start of the test (i.e., since τ=0). At 24 hours, record the reading given by the gas meter and/or the electrical energy meter, as appropriate. Determine the fossil fuel or electrical energy consumed during the entire 24-hour simulated use test and designate the quantity as Q.

6. Computations

6.1  Storage Tank and Heat Pump Water Heaters.

6.1.1  Storage Tank Capacity. The storage tank capacity is computed using the following:

Where:

V_st = the storage capacity of the water heater, gal (L).

W_f = the weight of the storage tank when completely filled with water, lb (kg).

W_t = the (tare) weight of the storage tank when completely empty, lb (kg).

ρ = the density of water used to fill the tank measured at the temperature of the water, lb/gal (kg/L).

6.1.2.  First-Hour Rating Computation. For the case in which the final draw is initiated at or prior to an elapsed time of one hour, the first-hour rating shall be computed using,

Where:

n = the number of draws that are completed during the first-hour rating test.

V*_i = the volume of water removed during the ith draw of the first-hour rating test, gal (L)

or, if the mass of water is being measured,

Where:

M*_i = the mass of water removed during the ith draw of the first-hour rating test, lb (kg).

ρ = the water density corresponding to the average outlet temperature measured during the ith draw, (T *_{del, I}), lb/gal (kg/L).

For the case in which a draw is not in progress at the elapsed time of one hour and a final draw is imposed at the elapsed time of one hour, the first-hour rating shall be calculated using

where n and V*_i are the same quantities as defined above, and

V*_n = the volume of water drawn during the nth (final) draw of the first-hour rating test, gal (L)

T *_del,n−1 = the average water outlet temperature measured during the (n−1)th draw of the first-hour rating test, °F (°C).

T *_del,n = the average water outlet temperature measured during the nth (final) draw of the first-hour rating test, °F (°C).

T *_min,n−1 = the minimum water outlet temperature measured during the (n−1)th draw of the first-hour rating test, °F (°C).

6.1.3  Recovery Efficiency. The recovery efficiency for gas, oil, and heat pump storage-type water heaters is computed as:

Where:

M₁ = total mass removed during the first draw of the 24-hour simulated use test, lb (kg), or, if the volume of water is being measured,

M₁ = V₁ ρ₁

Where:

V₁ = total volume removed during the first draw of the 24-hour simulated use test, gal (L).

ρ₁ = density of the water at the water temperature measured at the point where the flow volume is measured, lb/gal (kg/L).

C_p1 = specific heat of the withdrawn water, (T _del,1 + T _in,1) 2, Btu/lb °F (kJ/kg °C).

T _del,1 = average water outlet temperature measured during the first draw of the 24-hour simulated use test, °F (°C).

T _in,1 = average water inlet temperature measured during the first draw of the 24-hour simulated use test, °F (°C).

V_st = as defined in section 6.1.1.

ρ₂ = density of stored hot water, (T _max,1 + T _o)/2, lb/gal (kg/L).

C_p2 = specific heat of stored hot water evaluated at (T _max,1 + T _o) / 2, Btu/lb °F (kJ/kg₂ °C).

T _max,1 = maximum mean tank temperature recorded after cut-out following the first draw of the 24-hour simulated use test, °F (°C).

T _o = maximum mean tank temperature recorded prior to the first draw of the 24-hour simulated use test, °F (°C).

Q_r = the total energy used by the water heater between cut-out prior to the first draw and cut-out following the first draw, including auxiliary energy such as pilot lights, pumps, fans, etc., Btu (kJ). (Electrical auxiliary energy shall be converted to thermal energy using the following conversion: 1 kWh = 3,412 Btu.)

The recovery efficiency for electric water heaters with immersed heating elements is assumed to be 98%.

6.1.4  Hourly Standby Losses. The hourly standby energy losses are computed as:

Where:

Q_hr = the hourly standby energy losses of the water heater, Btu/h (kJ/h).

Q_stby = the total energy consumed by the water heater between the time at which the maximum mean tank temperature is observed after the sixth draw and the end of the 24-hour test period, Btu (kJ).

V_st = as defined in section 6.1.1.

ρ = density of stored hot water, (T ₂₄ + T _su) / 2, lb/gal (kg/L).

C_p = specific heat of the stored water, (T ₂₄ + T _su) / 2, Btu/lb÷°F (kJ/kg÷°C).

T ₂₄ = the mean tank temperature at the end of the 24-hour simulated use test, °F (°C).

T _su = the maximum mean tank temperature observed after the sixth draw, °F (°C).

η_r = as defined in section 6.1.3.

τ_{stby, 1} = elapsed time between the time at which the maximum mean tank temperature is observed after the sixth draw and the end of the 24-hour simulated use test, h.

The standby heat loss coefficient for the tank is computed as:

Where:

UA = standby heat loss coefficient of the storage tank, Btu/h÷°F (kJ/h÷°C).

Q_hr = as defined in this section.

T _{t, stby,1}= overall average storage tank temperature between the time when the maximum mean tank temperature is observed after the sixth draw and the end of the 24-hour simulated use test, °F (°C).

T _{a, stby,1}= overall average ambient temperature between the time when the maximum mean tank temperature is observed after the sixth draw and the end of the 24-hour simulated use test, °F (°C).

6.1.5  Daily Water Heating Energy Consumption. The daily water heating energy consumption, Q_d, is computed as:

Where:

Q = total energy used by the water heater during the 24-hour simulated use test including auxiliary energy such as pilot lights, pumps, fans, etc., Btu (kJ). (Electrical auxiliary energy shall be converted to thermal energy using the following conversion: 1 kWh = 3,412 Btu.)

V_st = as defined in section 6.1.1.

ρ= density of the stored hot water, (T ₂₄ + T _o) / 2, lb/gal (kg/L).

C_p = specific heat of the stored water, (T ₂₄ + T _o) / 2, Btu/lb÷°F (kJ/kg÷°C).

T ₂₄ = mean tank temperature at the end of the 24-hour simulated use test, °F (°C).

T _o = mean tank temperature at the beginning of the 24-hour simulated use test, recorded one minute before the first draw is initiated, °F (°C).

η_r = as defined in section 6.1.3.

6.1.6  Adjusted Daily Water Heating Energy Consumption. The adjusted daily water heating energy consumption, Q_da, takes into account that the temperature difference between the storage tank and surrounding ambient air may not be the nominal value of 67.5 °F (135 °F–67.5 °F) or 37.5 °C (57.2 °C–19.7 °C) due to the 10 °F (5.6 °C) allowable variation in storage tank temperature, 135 °F ±5 °F (57.2 °C ±2.8 °C), and the 5 °F (2.8 °C) allowable variation in surrounding ambient temperature 65 °F (18.3 °C) to 70 °F (21.1 °C). The adjusted daily water heating energy consumption is computed as:

Qda = QD − [(T stby, 2 − T a, stby,2) − (135 °F − 67.5 °F)] UAτstby, 2

or Qda = QD − [(T stby, 2 − T a, stby, 2) − (57.2 °C − 19.7 °C)] UAτstby, 2

Where:

Q_da = the adjusted daily water heating energy consumption, Btu (kJ).

Q_d = as defined in section 6.1.5.

T _{stby, 2} = the mean tank temperature during the total standby portion, τ_{stby, 2}, of the 24-hour test, °F (°C).

T _{a, stby, 2} = the average ambient temperature during the total standby portion, τstby, 2, of the 24-hour test, °F (°C).

UA = as defined in section 6.1.4.

τ_{stby, 2} = the number of hours during the 24-hour simulated test when water is not being withdrawn from the water heater.

A modification is also needed to take into account that the temperature difference between the outlet water temperature and supply water temperature may not be equivalent to the nominal value of 77 °F (135 °F–58 °F) or 42.8 °C (57.2 °C–14.4 °C). The following equations adjust the experimental data to a nominal 77 °F (42.8 °C) temperature rise.

The energy used to heat water, Btu/day (kJ/day), may be computed as:

Where:

M_i = the mass withdrawn for the ith draw (i = 1 to 6), lb (kg).

C_pi = the specific heat of the water of the ith draw, Btu/lb÷ °F (kJ/kg÷ °C).

T _{del, i} = the average water outlet temperature measured during the ith draw (i=1 to 6), °F (°C).

T _{in, i} = the average water inlet temperature measured during the ith draw (i=1 to 6), °F (°C).

η_r = as defined in section 6.1.3.

The energy required to heat the same quantity of water over a 77 °F (42.8 °C) temperature rise, Btu/day (kJ/day), is:

The difference between these two values is:

Q_HWD = Q_{HW, 77°−F} −Q_HW

or Q_HWD = Q_{HW,42.8°−F} −Q_HW

which must be added to the adjusted daily water heating energy consumption value. Thus, the daily energy consumption value which takes into account that the temperature difference between the storage tank and ambient temperature may not be 67.5 °F (37.5 °C) and that the temperature rise across the storage tank may not be 77 °F (42.8 °C) is:

Q_dm = Q_da + Q_HWD

6.1.7  Energy Factor. The energy factor, Ef, is computed as:

or

Where:

Q_dm = the modified daily water heating energy consumption as computed in accordance with section 6.1.6, Btu (kJ).

M_i = the mass withdrawn for the ith draw (i = 1 to 6), lb (kg).

C_pi = the specific heat of the water of the ith draw, Btu/lb °F (kJ/kg °C).

6.1.8  Annual Energy Consumption. The annual energy consumption for storage-type and heat pump water heaters is computed as:

E_annual = 365 × Q_dm

Where:

Q_dm = the modified daily water heating energy consumption as computed in accordance with section 6.1.6, Btu (kJ).

365 = the number of days in a year.

6.2  Instantaneous Water Heaters.

6.2.1  Maximum GPM (L/min) Rating Computation. Compute the maximum gpm (L/min) rating as:

which may be expressed as:

Where:

M_10m = the mass of water collected during the 10-minute test, lb (kg).

T _del = the average delivery temperature, °F (°C).

T _in = the average inlet temperature, °F (°C).

ρ = the density of water at the average delivery temperature, lb/gal (kg/L).

If a water meter is used the maximum gpm (L/min) rating is computed as:

Where:

V_10m = the volume of water measured during the 10-minute test, gal (L).

T _del = as defined in this section.

T _in = as defined in this section.

6.2.2  Recovery Efficiency

6.2.2.1  Fixed Input Instantaneous Water Heaters. The recovery efficiency is computed as:

Where:

M₁ = total mass removed during the first draw of the 24-hour simulated use test, lb (kg), or, if the volume of water is being measured,

M₁ = V_1. ρ

Where:

V₁ = total volume removed during the first draw of the 24-hour simulated use test, gal (L).

ρ= density of the water at the water temperature measured at the point where the flow volume is measured, lb/gal (kg/L).

C_p1 = specific heat of the withdrawn water, (T _del,1 + T_in,1) / 2, Btu/lb °F (kJ/kg °C).

T _{del, 1} = average water outlet temperature measured during the first draw of the 24-hour simulated use test, °F (°C).

T _{in, 1} = average water inlet temperature measured during the first draw of the 24-hour simulated use test, °F (°C).

Q_r = the total energy used by the water heater between cut-out prior to the first draw and cut-out following the first draw, including auxiliary energy such as pilot lights, pumps, fans, etc., Btu (kJ). (Electrical auxiliary energy shall be converted to thermal energy using the following conversion: 1 kWh = 3,412 Btu.)

6.2.2.2  Variable Input Instantaneous Water Heaters. For instantaneous water heaters that have a variable firing rate, two recovery efficiency values are computed, one at the maximum input rate and one at the minimum input rate. The recovery efficiency used in subsequent computations is taken as the average of these two values. The maximum recovery efficiency is computed as:

Where:

M₁ = as defined in section 6.2.2.1.

C_p1 = as defined in section 6.2.2.1.

T _{del, 1} = as defined in section 6.2.2.1.

T _{in, 1} = as defined in section 6.2.2.1.

Q_{r, max} = the total energy used by the water heater between burner cut-out prior to the first draw and burner cut-out following the first draw, including auxiliary energy such as pilot lights, Btu (kJ).

The minimum recovery efficiency is computed as:

Where:

M₄ = the mass withdrawn during the fourth draw, lb (kg), or, if the volume of water is being measured,

M₄ = V₄ ρ

Where:

V₄ = total volume removed during the first draw of the 24-hour simulated use test, gal (L).

ρ = as defined in 6.2.2.1

C_p4 = the specific heat of water, Btu/lb °F (kJ/kg °C).

T _{del, 4} = the average delivery temperature for the fourth draw, °F (°C).

T _{in, 4} = the average inlet temperature for the fourth draw, °F (°C).

Q_{r, min} = the total energy consumed between the beginning of the fourth draw and burner cut-out following the fourth draw, including auxiliary energy such as pilot lights, Btu (kJ).

The recovery efficiency is computed as:

Where:

η_r,max = as calculated above.

η_r,min = as calculated above.

6.2.3  Daily Water Heating Energy Consumption. The daily water heating energy consumption, Q_d, is computed as:

Qd = Q

Where:

Q = the energy used by the instantaneous water heater during the 24-hr simulated use test.

A modification is needed to take into account that the temperature difference between the outlet water temperature and supply water temperature may not be equivalent to the nominal value of 77 °F (135 °F−58 °F) or 42.8 °C (57.2 °C−14.4 °C). The following equations adjust the experimental data to a nominal 77 °F (42.8 °C) temperature rise.

The energy used to heat water may be computed as:

Where:

M_i = the mass withdrawn during the ith draw, lb (kg).

C_pi = the specific heat of water of the ith draw, Btu/lb °F (kJ/kg (°C).

T _del,i = the average delivery temperature of the ith draw, °F (°C).

T _in,i = the average inlet temperature of the ith draw, °F (°C).

η_r = as calculated in section 6.2.2.2.

The energy required to heat the same quantity of water over a 77 °F (42.8 °C) temperature rise is:

Where:

M_i = the mass withdrawn during the ith draw, lb (kg).

C_pi = the specific heat of water of the ith draw, Btu/lb °F (kJ/kg (°C).

η_r = as calculated above.

The difference between these two values is:

QHWD = QHW, 77 °F − QHW

or QHWD = QHW, 42.8 °C − QHW

which much be added to the daily water heating energy consumption value. Thus, the daily energy consumption value which takes into account that the temperature rise across the storage tank may not be 77 °F (42.8 °C) is:

Qdm = Qd + QHWD

6.2.4  Energy Factor. The energy factor, E_f, is computed as:

Where:

Q_dm = the daily water heating energy consumption as computed in accordance with section 6.2.3, Btu (kJ).

M_i = the mass associated with the ith draw, lb (kg).

C_pi = the specific heat of water computed at a temperature of (58 °F + 135 °F) / 2, Btu/lb °F [(14.4 °C + 57.2 °C) / 2, kJ/kg °C].

6.2.5  Annual Energy Consumption. The annual energy consumption for instantaneous type water heaters is computed as:

Eannual = 365 × Qdm

Where:

Q_dm = the modified daily energy consumption, Btu/day (kJ/day).

365 = the number of days in a year.

7. Ratings for Untested Models

In order to relieve the test burden on manufacturers who offer water heaters which differ only in fuel type or power input, ratings for untested models may be established in accordance with the following procedures. In lieu of the following procedures a manufacturer may elect to test the unit for which a rating is sought.

7.1  Gas Water Heaters. Ratings obtained for gas water heaters using natural gas can be used for an identical water heater which utilizes propane gas if the input ratings are within ±10%.

7.2  Electric Water Heaters

7.2.1  First-Hour Rating. If an electric storage-type water heater is available with more than one input rating, the manufacturer shall designate the standard input rating, and the water heater need only be tested with heating elements at the designated standard input ratings. The first-hour ratings for units having power input rating less than the designated standard input rating shall be assigned a first-hour rating equivalent to the first draw of the first-hour rating for the electric water heater with the standard input rating. For units having power inputs greater than the designated standard input rating, the first-hour rating shall be equivalent to that measured for the water heater with the standard input rating.

7.2.2  Energy Factor. The energy factor for identical electric storage-type water heaters, with the exception of heating element wattage, may use the energy factor obtained during testing of the water heater with the designated standard input rating.

[63 FR 26008, May 11, 1998; 63 FR 38738, July 20, 1998, as amended at 66 FR 4497, Jan. 17, 2001]

1. Test method. The test method for testing room air conditioners shall consist of application of the methods and conditions in American National Standard (ANS) Z234.1–1972, “Room Air Conditioners,” sections 4, 5, 6.1, and 6.5, and in American Society of Heating, Refrigerating and Air Conditioning in Engineers (ASHRAE) Standard 16–69, “Method of Testing for Rating Room Air Conditioners.”

2. Test conditions. Establish the test conditions described in sections 4 and 5 of ANS Z234.1–1972 and in accordance with ASHRAE Standard 16–69.

3. Measurements. Measure the quantities delineated in section 5 of ANS Z234.1–1972.

4. Calculations. 4.1 Calculate the cooling capacity (expressed in Btu/hr) as required in section 6.1 of ANS Z234.1–1972 and in accordance with ASHRAE Standard 16–69.

4.2  Determine the electrical power input (expressed in watts) as required by section 6.5 of ANS Z234.1–1972 and in accordance with ASHRAE Standard 16–69.

[42 FR 27898, June 1, 1977. Redesignated and amended at 44 FR 37938, June 29, 1979]

1. Testing conditions.

1.1  Installation.

1.1.1  Electric heater. Install heater according to manufacturer's instructions. Heaters shall be connected to an electrical supply circuit of nameplate voltage with a wattmeter installed in the circuit. The wattmeter shall have a maximum error not greater than one percent.

1.1.2  Unvented gas heater. Install heater according to manufacturer's instructions. Heaters shall be connected to a gas supply line with a gas displacement meter installed between the supply line and the heater according to manufacturer's specifications. The gas displacement meter shall have a maximum error not greater than one percent. Gas heaters with electrical auxiliaries shall be connected to an electrical supply circuit of nameplate voltage with a wattmeter installed in the circuit. The wattmeter shall have a maximum error not greater than one percent.

1.1.3  Unvented oil heater. Install heater according to manufacturer's instructions. Oil heaters with electric auxiliaries shall be connected to an electrical supply circuit of nameplate voltage with a wattmeter installed in the circuit. The wattmeter shall have a maximum error not greater than one percent.

1.2  Temperature regulating controls. All temperature regulating controls shall be shorted out of the circuit or adjusted so that they will not operate during the test period.

1.3  Fan controls. All fan controls shall be set at the highest fan speed setting.

1.4  Energy supply.

1.4.1  Electrical supply. Supply power to the heater within one percent of the nameplate voltage.

1.4.2  Natural gas supply. For an unvented gas heater utilizing natural gas, maintain the gas supply to the heater with a normal inlet test pressure immediately ahead of all controls at 7 to 10 inches of water column. The regulator outlet pressure at normal supply test pressure shall be approximately that recommended by the manufacturer. The natural gas supplied should have a higher heating value within ±5 percent of 1,025 Btu's per standard cubic foot. Determine the higher heating value, in Btu's per standard cubic foot, for the natural gas to be used in the test, with an error no greater than one percent. Alternatively, the test can be conducted using “bottled” natural gas of a higher heating value within ±5 percent of 1,025 Btu's per standard cubic foot as long as the actual higher heating value of the bottled natural gas has been determined with an error no greater than one percent as certified by the supplier.

1.4.3  Propane gas supply. For an unvented gas heater utilizing propane, maintain the gas supply to the heater with a normal inlet test pressure immediately ahead of all controls at 11 to 13 inches of water column. The regulator outlet pressure at normal supply test pressure shall be that recommended by the manufacturer. The propane supplied should have a higher heating value of within±5 percent of 2,500 Btu's per standard cubic foot. Determine the higher heating value in Btu's per standard foot, for the propane to be used in the test, with an error no greater than one percent. Alternatively, the test can be conducted using “bottled” propane of a higher heating value within ±5 percent of 2,500 Btu's per standard cubic foot as long as the actual higher heating value of the bottled propane has been determined with an error no greater than one percent as certified by the supplier.

1.4.4  Oil supply. For an unvented oil heater utilizing kerosene, determine the higher heating value in Btu's per gallon with an error no greater than one percent. Alternatively, the test can be conducted using a tested fuel of a higher heating value within ±5 percent of 137,400 Btu's per gallon as long as the actual higher heating value of the tested fuel has been determined with an error no greater than one percent as certified by the supplier.

1.5  Energy flow instrumentation. Install one or more energy flow instruments which measure, as appropriate and with an error no greater than one percent, the quantity of electrical energy, natural gas, propane gas, or oil supplied to the heater.

2. Testing and measurements.

2.1  Electric power measurement. Establish the test conditions set forth in section 1 of this appendix. Allow an electric heater to warm up for at least five minutes before recording the maximum electric power measurement from the wattmeter. Record the maximum electric power (P_E) expressed in kilowatts.

Allow the auxiliary electrical system of a forced air unvented gas, propane, or oil heater to operate for at least five minutes before recording the maximum auxiliary electric power measurement from the wattmeter. Record the maximum auxiliary electric power (P_A) expressed in kilowatts.

2.2  Natural gas, propane, and oil measurement. Establish the test conditions as set forth in section 1 of this appendix. A natural gas, propane, or oil heater shall be operated for one hour. Using either the nameplate rating or the energy flow instrumentation set forth in section 1.5 of this appendix and the fuel supply rating set forth in sections 1.4.2, 1.4.3, or 1.4.4 of this appendix, as appropriate, determine the maximum fuel input (P_F) of the heater under test in Btu's per hour. The energy flow instrumentation shall measure the maximum fuel input with an error no greater than one percent.

3. Calculations.

3.1  Annual energy consumption for primary electric heaters. For primary electric heaters, calculate the annual energy consumption (E_E) expressed in kilowatt-hours per year and defined as:

E_E=2080(0.77)DHR

where:

2080=national average annual heating load hours

0.77=adjustment factor

DHR=design heating requirement and is equal to P_E/1.2 in kilowatts.

P_E=as defined in 2.1 of this appendix

1.2=typical oversizing factor for primary electric heaters

3.2  Annual energy consumption for primary electric heaters by geographic region of the United States. For primary electric heaters, calculate the annual energy consumption by geographic region of the United States (E_R) expressed in kilowatt-hours per year and defined as:

E_R=HLH(0.77) (DHR)

where:

HLH=heating load hours for a specific region determined from Figure 1 of this appendix in hours

0.77=as defined in 3.1 of this appendix

DHR=as defined in 3.1 of this appendix

3.3  Rated output for electric heaters. Calculate the rated output (Q_out) for electric heaters, expressed in Btu's per hour, and defined as:

Q_out=P_E (3,412 Btu/kWh)

where:

P_E=as defined in 2.1 of this appendix

3.4  Rated output for unvented heaters using either natural gas, propane, or oil. For unvented heaters using either natural gas, propane, or oil equipped without auxiliary electrical systems, the rated output (Q_out), expressed in Btu's per hour, is equal to P_F, as determined in section 2.2 of this appendix.

For unvented heaters using either natural gas, propane, or oil equipped with auxiliary electrical systems, calculate the rated output (Q_out), expressed in Btu's per hour, and defined as:

Q_out=P_F+P_A (3,412 Btu/kWh)

where:

P_F=as defined in 2.2 of this appendix in Btu/hr

P_A=as defined in 2.1 of this appendix in Btu/hr

(Energy Policy and Conservation Act, Pub. L. 94–163, as amended by Pub. L. 94–385; Federal Energy Administration Act of 1974, Pub. L. 93–275, as amended by Pub. L. 94–385; Department of Energy Organization Act, Pub. L. 95–91; E.O. 11790, 39 FR 23185)

[43 FR 20132, May 10, 1978. Redesignated and amended at 44 FR 37938, June 29, 1979; 49 FR 12157, Mar. 28, 1984]

1. Definitions

1.1  “IRE-unit flat field” means a specific video electrical signal which results in a particular level of brightness of the television screen as established by the Institute of Radio Engineers.

1.2  “Filament keep-warm” means a feature that provides a voltage to keep vacuum tube and/or picture tube filaments warm for the purpose of allowing almost instantaneous response to the power control switch.

1.3  “Operating time” (to) means the hours per year during which the television set is operating with power control turned on.

1.4  “Remote control” means an optional feature which allows the user to control the television set from more than one location by a hand held device.

1.5  “Standby power consumption” (Ps) means the minimum amount of energy consumed with the power control switch turned off.

1.6  “Standby time” (ts) means the hours per year during which the television set is connected to a power outlet with the power control switch turned off.

1.7  “Vacation switch or master on-off switch” means an optional energy saving feature incorporated into the design of a television set that permits the user to disconnect the filament keep-warm circuit(s).

1.8  “Remote control defeat switch” means a switch which permits the user to disconnect all standby power to a television set.

2. Testing Conditions and Measurements

2.1  Test equipment and test signals. The following equipment and test signals shall be used for testing of television sets.

2.1.1  Regulated power source capable of supplying 120 volts (±1.2 volts) alternating current.

2.1.2  Signal generator capable of producing radio frequency (RF) television test signals, at a convenient very high frequency (VHF) channel, modulated with, National Television System Committee composite video as follows:

2.1.2.1  Standard White Pattern, RF signal modulated to 87 percent with a 100 IRE-unit flat field.

2.1.2.2  Standard Black Pattern, all adjustments as for 2.1.2.1 except modulated with a zero IRE-unit flat field.

2.1.2.3  The test signals in 2.1.2.1 and 2.1.2.2, supplied by a source whose impedance equals the design antenna impedance of the television set under test, shall be adjusted to a level of 70 decibels (dB) ±3dB, referred to a zero dB level of one femtowatt (1×10⁻¹⁵ watt) available power. (For a 300 ohm source, 70 dB referred to one femtowatt corresponds to an open-circuit voltage of 3.5 millivolts. For the calculation of “available power” use American National Standard C.16.13–1961, Method of Testing Monochrome Television Broadcast Receivers.)

2.1.3  Wattmeter capable of measuring the average power consumption of the television set under test. The wattmeter shall be accurate to within 1 percent of the full scale value. All measurements shall be made on the upper half of the scale of the wattmeter.

2.2  Initial set-up of television set.

2.2.1  Remove all batteries from television sets designed for both battery and alternating current operation. Deactivate all present or automatic controls affecting brightness which are customer options. Adjust all non-customer controls according to the manufacturer's service procedure.

2.2.2  Apply power to the television set under test from the power source specified in 2.1.1 through the wattmeter specified in 2.1.3. Adjust the volume control to the lowest possible setting.

2.2.3  Connect the output of the signal generator as specified in 2.1.2 to the VHF antenna terminals of the television set. Tune the television set to the channel of the RF signal.

2.3  Measurement of operating power consumption (Po)

2.3.1  Turn on the television set and allow at least five minutes warm-up time. With the synchronization controls adjusted for a stable test pattern, apply the standard white pattern specified in 2.1.2.1 to the television set. Adjust any customer controls other than the volume or synchronization controls for maximum power consumption as indicated by the wattmeter specified in 2.1.3. Illuminate any room illuminance sensor which has not been deactivated, to produce maximum power consumption. Record the white pattern consumption (Pw) as indicated by the wattmeter in watts.

2.3.2  Change the signal source to the standard black pattern specified in 2.1.2.2. Adjust any customer controls, other than the volume or synchronization controls, for the minimum power consumption as indicated by the wattmeter. Cover any room illuminance sensor which has not been deactivated. Record the black pattern power consumption (Pb) as indicated by the wattmeter in watts.

2.3.3  Compute the operating power consumption (po) as follows:

Po=(Pw+Pb/2)

where

Po=operating power consumption in watts

Pw=as determined from 2.3.1

Pb=as determined from 2.3.2

2.2  Measurements of standby power consumption (Ps)

2.4.1  For television sets without either a vacation switch or a remote control defeat switch, turn the power switch off and after two minutes measure the standby power consumption (P).

2.4.2  For a television set equipped with a remote control defeat switch, a vacation switch or both, turn the power switch, any vacation switch, and any remote er consumptions, (Pmax). The standby power is then calculated from the equation:

Ps=[(P_max−P_min)/2]+P_min

where

Ps=standby power consumption in watts

P_max=power consumption, in watts, measured with the television set power switch off and the vacation switch and remote control defeat switch in the highest energy consuming position.

P_min=power consumption, in watts, measured with the television set power switch off and the vacation switch and remote control defeat switch in the lowest energy consuming position.

3.0  Average Annual Energy Consumption

E=(Poto/1,000)+(Psts/1,000)=2.2Po+6.56Ps

where

E=total average energy consumed by the television set (kilowatt-hour per year)

Po=operating power consumption as computed in 2.3.3

to=operating time, 2,200 h/yr

Ps=standby power consumption computed in 2.4

ts=standby time, 6,560 h/yr

[42 FR 46154, Sept. 14, 1977. Redesignated and amended at 44 FR 37938, June 29, 1979]

1. Definitions

1.1  Built-in means the product is supported by surrounding cabinetry, walls, or other similar structures.

1.2  Drop-in means the product is supported by horizontal surface cabinetry.

1.3  Forced convection means a mode of conventional oven operation in which a fan is used to circulate the heated air within the oven compartment during cooking.

1.4  Freestanding means the product is not supported by surrounding cabinetry, walls, or other similar structures.

1.5  IEC 705 refers to the test standard published by the International Electrotechnical Commission, entitled “Method for Measuring the Performance of Microwave Ovens for Household and Similar Purposes,” Publication 705–1988 and Amendment 2—1993. (See 10 CFR 430.22)

1.6  Normal nonoperating temperature means the temperature of all areas of an appliance to be tested are within 5 °F (2.8 °C) of the temperature that the identical areas of the same basic model of the appliance would attain if it remained in the test room for 24 hours while not operating with all oven doors closed and with any gas pilot lights on and adjusted in accordance with manufacturer's instructions.

1.7  Primary energy consumption means either the electrical energy consumption of a conventional electric oven or the gas energy consumption of a conventional gas oven.

1.8  Secondary energy consumption means any electrical energy consumption, other than clock energy consumption, of a conventional gas oven.

1.9  Standard cubic foot (L) of gas means that quantity of gas that occupies 1 cubic foot (L) when saturated with water vapor at a temperature of 60 °F (15.6 °C) and a pressure of 30 inches of mercury (101.6 kPa) (density of mercury equals 13.595 grams per cubic centimeter).

1.10  Thermocouple means a device consisting of two dissimilar metals which are joined together and, with their associated wires, are used to measure temperature by means of electromotive force.

1.11  Symbol Usage. The following identity relationships are provided to help clarify the symbology used throughout this procedure.

A—Number of Hours in a Year

B—Number of Hours Pilot Light Contributes to Cooking

C—Specific Heat

E—Energy Consumed

Eff—Cooking Efficiency

H—Heating Value of Gas

K—Conversion for Watt-hours to Kilowatt hours

K_e—3.412 Btu/Wh, Conversion for Watt-hours to Btu's

M—Mass

n—Number of Units

O—Annual Useful Cooking Energy Output

P—Power

Q—Gas Flow Rate

R—Energy Factor, Ratio of useful Cooking Energy Output to Total Energy Input

S—Number of Self Cleaning Operations per Year

T—Temperature

t—Time

V—Volume of Gas Consumed

W—Weight of Test Block

2. Test Conditions

2.1  Installation. A free standing kitchen range shall be installed with the back directly against, or as near as possible to, a vertical wall which extends at least 1 foot above and on either side of the appliance. There shall be no side walls. A drop-in, built-in or wall-mounted appliance shall be installed in an enclosure in accordance with the manufacturer's instructions. These appliances are to be completely assembled with all handles, knobs, guards and the like mounted in place. Any electric resistance heaters, gas burners, baking racks, and baffles shall be in place in accordance with the manufacturer's instructions; however, broiler pans are to be removed from the oven's baking compartment. Disconnect any electrical clock which uses energy continuously, except for those that are an integral part of the timing or temperature controlling circuit of the oven, cooktop, or microwave oven. Do not disconnect or modify the circuit to any other electrical devices or features.

2.1.1  Conventional electric ranges, ovens, and cooking tops. These products shall be connected to an electrical supply circuit with voltage as specified in Section 2.2.1 with a watt-hour meter installed in the circuit. The watt-hour meter shall be as described in Section 2.9.1.1.

2.1.2  Conventional gas ranges, ovens, and cooking tops. These products shall be connected to a gas supply line with a gas meter installed between the supply line and the appliance being tested, according to manufacturer's specifications. The gas meter shall be as described in Section 2.9.2. Conventional gas ranges, ovens and cooking tops with electrical ignition devices or other electrical components shall be connected to an electrical supply circuit of nameplate voltage with a watt-hour meter installed in the circuit. The watt-hour meter shall be as described in Section 2.9.1.1.

2.1.3  Microwave ovens. Install the microwave oven in accordance with the manufacturer's instructions and connect to an electrical supply circuit with voltage as specified in Section 2.2.1. A watt-hour meter and watt meter shall be installed in the circuit and shall be as described in Section 2.9.1.1 and 2.9.1.2. If trial runs are needed to set the “on” time for the test, the test measurements are to be separated according to Section 4, Paragraph 12.6 of IEC 705 Amendment 2. (See 10 CFR 430.22)

2.2  Energy supply.

2.2.1  Electrical supply. Maintain the electrical supply to the conventional range, conventional cooking top, and conventional oven being tested at 240/120 volts except that basic models rated only at 208/120 volts shall be tested at that rating. Maintain the voltage within 2 percent of the above specified voltages. For the microwave oven testing, however, maintain the electrical supply to a microwave oven at 120 volts ±1 volt and at 60 hertz.

2.2.2  Gas supply.

2.2.2.1  Gas burner adjustments. Conventional gas ranges, ovens, and cooking tops shall be tested with all of the gas burners adjusted in accordance with the installation or operation instructions provided by the manufacturer. In every case, the burner must be adjusted with sufficient air flow to prevent a yellow flame or a flame with yellow tips.

2.2.2.2  Natural gas. For testing convertible cooking appliances or appliances which are designed to operate using only natural gas, maintain the natural gas pressure immediately ahead of all controls of the unit under test at 7 to 10 inches of water column (1743.6 to 2490.8 Pa). The regulator outlet pressure shall equal the manufacturer's recommendation. The natural gas supplied should have a heating value of approximately 1,025 Btu's per standard cubic foot (38.2 kJ/L). The actual gross heating value, H_n, in Btu's per standard cubic foot (kJ/L), for the natural gas to be used in the test shall be obtained either from measurements made by the manufacturer conducting the test using equipment that meets the requirements described in Section 2.9.4 or by the use of bottled natural gas whose gross heating value is certified to be at least as accurate a value that meets the requirements in Section 2.9.4.

2.2.2.3  Propane. For testing convertible cooking appliances with propane or for testing appliances which are designed to operate using only LP-gas, maintain the propane pressure immediately ahead of all controls of the unit under test at 11 to 13 inches of water column (2740 to 3238 Pa). The regulator outlet pressure shall equal the manufacturer's recommendation. The propane supplied should have a heating value of approximately 2,500 Btu's per standard cubic foot (93.2 kJ/L). The actual gross heating value, H_p, in Btu's per standard cubic foot (kJ/L), for the propane to be used in the test shall be obtained either from measurements made by the manufacturer conducting the test using equipment that meets the requirements described in Section 2.9.4 or by the use of bottled propane whose gross heating value is certified to be at least as accurate a value that meets the requirements described in Section 2.9.4.

2.2.2.4  Test gas. A basic model of a convertible cooking appliance shall be tested with natural gas, but may also be tested with propane. Any basic model of a conventional range, conventional cooking top, or conventional oven which is designed to operate using only natural gas as the energy source must be tested with natural gas. Any basic model of a conventional range, conventional cooking top, or conventional oven which is designed to operate using only LP gas as the gas energy source must be tested with propane gas.

2.3  Air circulation. Maintain air circulation in the room sufficient to secure a reasonably uniform temperature distribution, but do not cause a direct draft on the unit under test.

2.4  Setting the conventional oven thermostat.

2.4.1  Conventional electric oven. Install a thermocouple approximately in the center of the usable baking space. Provide a temperature indicator system for measuring the oven's temperature with an accuracy as indicated in Section 2.9.3.2. If the oven thermostat does not cycle on and off, adjust or determine the conventional electric oven thermostat setting to provide an average internal temperature which is 325°±5 °F (180.6° ±2.8 °C) higher than the room ambient air temperature. If the oven thermostat operates by cycling on and off, adjust or determine the conventional electric oven thermostat setting to provide an average internal temperature which is 325° ±5 °F (180.6°±2.8 °C) higher than the room ambient air temperature. This shall be done by measuring the maximum and minimum temperatures in any three consecutive cut-off/cut-on actions of the electric resistance heaters, excluding the initial cut-off/cut-on action, by the thermostat after the temperature rise of 325°±5 °F (180.6° ±2.8 °C) has been attained by the conventional electric oven. Remove the thermocouple after the thermostat has been set.

2.4.2  Conventional gas oven. Install five parallel-connected weighted thermocouples, one located at the center of the conventional gas oven's usable baking space and the other four equally spaced between the center and the corners of the conventional gas oven on the diagonals of a horizontal plane through the center of the conventional gas oven. Each weighted thermocouple shall be constructed of a copper disc that is 1-inch (25.4 mm) in diameter and 1/8-inch (3.2 mm) thick. The two thermocouple wires shall be located in two holes in the disc spaced 1/2-inch (12.7 mm) apart, with each hole being located 1/4-inch (6.4 mm) from the center of the disc. Both thermocouple wires shall be silver-soldered to the copper disc. Provide a temperature indicator system for measuring the oven's temperature with an accuracy as indicated in Section 2.9.3.2. If the oven thermostat does not cycle on or off, adjust or determine the conventional gas oven thermostat setting to provide an average internal temperature which is 325 °±5 °F (180.6 °±2.8 °C) higher than the room ambient air temperature. If the oven thermostat operates by cycling on and off, adjust or determine the conventional gas oven thermostat setting to provide an average internal temperature which is 325°±5 °F (180.6±2.8 °C) higher than the room ambient air temperature. This shall be done by measuring the maximum and minimum temperatures in any three consecutive cut-off/cut-on actions of the gas burners, excluding the initial cut-off/cut-on action, by the thermostat after the temperature rise of 325°±5 °F (180.6 °±2.8 °C) has been attained by the conventional gas oven. Remove the thermocouples after the thermostat has been set.

2.5  Ambient room air temperature. During the test, maintain an ambient room air temperature, T_R, of 77°±9 °F (25°±5 °C) for conventional ovens and cooking tops, or as indicated in Section 4, Paragraph 12.4 of IEC 705 Amendment 2 for microwave ovens, as measured at least 5 feet (1.5 m) and not more than 8 feet (2.4 m) from the nearest surface of the unit under test and approximately 3 feet (0.9 m) above the floor. The temperature shall be measured with a thermometer or temperature indicating system with an accuracy as specified in Section 2.9.3.1.

2.6  Normal nonoperating temperature. All areas of the appliance to be tested shall attain the normal nonoperating temperature, as defined in Section 1.6, before any testing begins. The equipment for measuring the applicable normal nonoperating temperature shall be as described in Sections 2.9.3.1, 2.9.3.2, 2.9.3.3, 2.9.3.4, and 2.9.3.5, as applicable.

2.7  Test blocks for conventional oven and cooking top. The test blocks shall be made of aluminum alloy No. 6061, with a specific heat of 0.23 Btu/lb- °F (0.96 kJ/[kg ÷ °C]) and with any temper that will give a czoefficient of thermal conductivity of 1073.3 to 1189.1 Btu-in/h-ft² - °F (154.8 to 171.5 W/[m ÷ °C]). Each block shall have a hole at its top. The hole shall be 0.08 inch (2.03 mm) in diameter and 0.80 inch (20.3 mm) deep. The manufacturer conducting the test may provide other means which will ensure that the thermocouple junction is installed at this same position and depth.

The bottom of each block shall be flat to within 0.002 inch (0.051 mm) TIR (total indicator reading). Determine the actual weight of each test block with a scale with an accuracy as indicated in Section 2.9.5.

2.7.1  Conventional oven test block. The test block for the conventional oven, W₁, shall be 6.25±0.05 inches (158.8±1.3 mm) in diameter, approximately 2.8 inches (71 mm) high and shall weigh 8.5±0.1 lbs (3.86±0.05 kg). The block shall be finished with an anodic black coating which has a minimum thickness of 0.001 inch (0.025 mm) or with a finish having the equivalent absorptivity.

2.7.2  Small test block for conventional cooking top. The small test block, W₂, shall be 6.25±0.05 inches (158.8±1.3 mm) in diameter, approximately 2.8 inches (71 mm) high and shall weigh 8.5±0.1 lbs (3.86±0.05 kg).

2.7.3  Large test block for conventional cooking top. The large test block for the conventional cooking top, W₃, shall be 9±0.05 inches (228.6±1.3 mm) in diameter, approximately 3.0 inches (76 mm) high and shall weigh 19±0.1 lbs (8.62±0.05 kg).

2.7.4  Thermocouple installation. Install the thermocouple such that the thermocouple junction (where the thermocouple contacts the test block) is at the bottom of the hole provided in the test block and that the thermocouple junction makes good thermal contact with the aluminum block. If the test blocks are to be water cooled between tests the thermocouple hole should be sealed, or other steps taken, to insure that the thermocouple hole is completely dry at the start of the next test. Provide a temperature indicator system for measuring the test block temperature with an accuracy as indicated in Section 2.9.3.3.

2.7.5  Initial test block temperature. Maintain the initial temperature of the test blocks, T_I, within ±4 °F (±2.2 °C) of the ambient room air temperature as specified in Section 2.5. If the test block has been cooled (or heated) to bring it to room temperature, allow the block to stabilize for at least 2 minutes after removal from the cooling (or heating) source, before measuring its initial temperature.

2.8  Microwave oven test load.

2.8.1  Test container. The test container shall be as specified in Section 4, Paragraph 12.2 of IEC 705 Amendment 2.

2.8.2  Test water load. The test water load shall be as specified in Section 4, Paragraph 12.1 of IEC 705 Amendment 2.

2.8.2.1  Test water load and test container temperature. Before the start of the test, the oven and the test container shall be at ambient temperature as specified in Section 4, Paragraph 12.4 of IEC 705 Amendment 2. The test water load shall be contained in a chiller (not the test container) and maintained at 18° ±1.8 °F (10° ±1 °C) below the ambient room temperature.

2.9  Instrumentation. Perform all test measurements using the following instruments, as appropriate:

2.9.1  Electrical Measurements.

2.9.1.1  Watt-hour meter. The watt-hour meter for measuring the electrical energy consumption of conventional ovens and cooking tops shall have a resolution of 1 watt-hour (3.6 kJ) or less and a maximum error no greater than 1.5 percent of the measured value for any demand greater than 100 watts. The watt-hour meter for measuring the energy consumption of microwave ovens shall have a resolution of 0.1 watt-hour (0.36 kJ) or less and a maximum error no greater than 1.5 percent of the measured value.

2.9.1.2  Watt meter. The watt meter used to measure the conventional oven, conventional range, range clock power or the power input of the microwave oven shall have a resolution of 0.2 watt (0.2 J/s) or less and a maximum error no greater than 5 percent of the measured value.

2.9.2  Gas Measurements.

2.9.2.1  Positive displacement meters. The gas meter to be used for measuring the gas consumed by the gas burners of the oven or cooking top shall have a resolution of 0.01 cubic foot (0.28 L) or less and a maximum error no greater than 1 percent of the measured value for any demand greater than 2.2 cubic feet per hour (62.3 L/h). If a positive displacement gas meter is used for measuring the gas consumed by the pilot lights, it shall have a resolution of at least 0.01 cubic foot (0.28 L) or less and have a maximum error no greater than 2 percent of the measured value.

2.9.2.2  Flow meter. If a gas flow meter is used for measuring the gas consumed by the pilot lights, it shall be calibrated to have a maximum error no greater than 1.5 percent of the measured value and a resolution of 1 percent or less of the measured value.

2.9.3  Temperature measurement equipment.

2.9.3.1  Room temperature indicating system. The room temperature indicating system shall be as specified in Section 4, Paragraph 12.3 of IEC 705 Amendment 2 for microwave ovens and Section 2.9.3.5 for ranges, ovens and cooktops.

2.9.3.2  Temperature indicator system for measuring conventional oven temperature. The equipment for measuring the conventional oven temperature shall have an error no greater than ±4 °F (±2.2 °C) over the range of 65° to 500 °F (18 °C to 260 °C).

2.9.3.3  Temperature indicator system for measuring test block temperature. The system shall have an error no greater than ±2 °F (±1.1 °C) when measuring specific temperatures over the range of 65° to 330 °F (18.3 °C to 165.6 °C). It shall also have an error no greater than ±2 °F (±1.1 °C) when measuring any temperature difference up to 240 °F (133.3 °C) within the above range.

2.9.3.4  Test load temperatures. The thermometer or other temperature measuring instrument used to measure the test water load temperature shall be as specified in Section 4, Paragraph 12.3 of IEC 705 Amendment 2. Use only one thermometer or other temperature measuring device throughout the entire test procedure.

2.9.3.5  Temperature indicator system for measuring surface temperatures. The temperature of any surface of an appliance shall be measured by means of a thermocouple in firm contact with the surface. The temperature indicating system shall have an error no greater than ±1 °F (±0.6°C) over the range 65° to 90 °F (18 °C to 32 °C).

2.9.4  Heating Value. The heating value of the natural gas or propane shall be measured with an instrument and associated readout device that has a maximum error no greater than ±0.5% of the measured value and a resolution of ±0.2% or less of the full scale reading of the indicator instrument. The heating value of natural gas or propane must be corrected for local temperature and pressure conditions.

2.9.5  Scale. The scale used for weighing the test blocks shall have a maximum error no greater than 1 ounce (28.4 g). The scale used for weighing the microwave oven test water load shall be as specified in Section 4, paragraph 12.3 of IEC 705 Amendment 2.

3. Test Methods and Measurements

3.1  Test methods.

3.1.1  Conventional oven. Perform a test by establishing the testing conditions set forth in Section 2, “TEST CONDITIONS,” of this Appendix, and adjust any pilot lights of a conventional gas oven in accordance with the manufacturer's instructions and turn off the gas flow to the conventional cooking top, if so equipped. Before beginning the test, the conventional oven shall be at its normal nonoperating temperature as defined in Section 1.6 and described in Section 2.6. Set the conventional oven test block W₁ approximately in the center of the usable baking space. If there is a selector switch for selecting the mode of operation of the oven, set it for normal baking. If an oven permits baking by either forced convection by using a fan, or without forced convection, the oven is to be tested in each of those two modes. The oven shall remain on for at least one complete thermostat “cut-off/cut-on” of the electrical resistance heaters or gas burners after the test block temperature has increased 234 °F (130 °C) above its initial temperature.

3.1.1.1  Self-cleaning operation of a conventional oven. Establish the test conditions set forth in Section 2, “TEST CONDITIONS,” of this Appendix. Adjust any pilot lights of a conventional gas oven in accordance with the manufacturer's instructions and turn off the gas flow to the conventional cooking top. The temperature of the conventional oven shall be its normal nonoperating temperature as defined in Section 1.6 and described in Section 2.6. Then set the conventional oven's self-cleaning process in accordance with the manufacturer's instructions. If the self-cleaning process is adjustable, use the average time recommended by the manufacturer for a moderately soiled oven.

3.1.1.2  Continuously burning pilot lights of a conventional gas oven. Establish the test conditions set forth in Section 2, “TEST CONDITIONS,” of this Appendix. Adjust any pilot lights of a conventional gas oven in accordance with the manufacturer's instructions and turn off the gas flow to the conventional cooking top. If a positive displacement gas meter is used the, test duration shall be sufficient to measure a gas consumption which is at least 200 times the resolution of the gas meter.

3.1.2  Conventional cooking top. Establish the test conditions set forth in Section 2, “TEST CONDITIONS,” of this Appendix. Adjust any pilot lights of a conventional gas cooking top in accordance with the manufacturer's instructions and turn off the gas flow to the conventional oven(s), if so equipped. The temperature of the conventional cooking top shall be its normal nonoperating temperature as defined in Section 1.6 and described in Section 2.6. Set the test block in the center of the surface unit under test. The small test block, W₂, shall be used on electric surface units of 7 inches (178 mm) or less in diameter. The large test block, W₃, shall be used on electric surface units over 7 inches (177.8 mm) in diameter and on all gas surface units. Turn on the surface unit under test and set its energy input rate to the maximum setting. When the test block reaches 144 °F (80 °C) above its initial test block temperature, immediately reduce the energy input rate to 25±5 percent of the maximum energy input rate. After 15±0.1 minutes at the reduced energy setting, turn off the surface unit under test.

3.1.2.1  Continuously burning pilot lights of a conventional gas cooking top. Establish the test conditions set forth in Section 2, “TEST CONDITIONS,” of this Appendix. Adjust any pilot lights of a conventional gas cooking top in accordance with the manufacturer's instructions and turn off the gas flow to the conventional oven(s). If a positive displacement gas meter is used, the test duration shall be sufficient to measure a gas consumption which is at least 200 times the resolution of the gas meter.

3.1.3  Microwave oven.

3.1.3.1  Microwave oven test energy or power output. Establish the testing conditions set forth in Section 2, “TEST CONDITIONS,” of this Appendix. Follow the test procedure as specified in Section 4, Paragraph 12.4 of IEC 705 Amendment 2.

3.2  Test measurements.

3.2.1  Conventional oven test energy consumption. If the oven thermostat controls the oven temperature without cycling on and off, measure the energy consumed, E_O, when the temperature of the block reaches T_O (T_O is 234 °F (130 °C) above the initial block temperature, T_I). If the oven thermostat operates by cycling on and off, make the following series of measurements: Measure the block temperature, T_A, and the energy consumed, E_A, or volume of gas consumed, V_A, at the end of the last “ON” period of the conventional oven before the block reaches T_O. Measure the block temperature, T_B, and the energy consumed, E_B, or volume of gas consumed, V_B, at the beginning of the next “ON” period. Measure the block temperature, T_C, and the energy consumed, E_C, or volume of gas consumed, V_C, at the end of that “ON” period. Measure the block temperature, T_D, and the energy consumed, E_D, or volume of gas consumed, V_D, at the beginning of the following “ON” period. Energy measurements for E_O, E_A, E_B, E_C and E_D, should be expressed in watt-hours (kJ) for conventional electric ovens and volume measurements for V_A, V_B, V_C and V_D should be expressed in standard cubic feet (L) of gas for conventional gas ovens. For a gas oven, measure in watt-hours (kJ) any electrical energy, E_IO, consumed by an ignition device or other electrical components required for the operation of a conventional gas oven while heating the test block to T_O. The energy consumed by a continuously operating clock that is an integral part of the timing or temperature control circuit and cannot be disconnected during the test may be subtracted from the oven test energy to obtain the test energy consumption, E_O or E_IO.

3.2.1.1  Conventional oven average test energy consumption. If the conventional oven permits baking by either forced convection or without forced convection and the oven thermostat does not cycle on and off, measure the energy consumed with the forced convection mode, (E_O)₁, and without the forced convection mode, (E_O)₂, when the temperature of the block reaches T_O (T_O is 234 °F (130 °C) above the initial block temperature, T_I). If the conventional oven permits baking by either forced convection or without forced convection and the oven thermostat operates by cycling on and off, make the following series of measurements with and without the forced convection mode: Measure the block temperature, T_A, and the energy consumed, E_A, or volume of gas consumed, V_A, at the end of the last “ON” period of the conventional oven before the block reaches T_O. Measure the block temperature, T_B, and the energy consumed, E_B, or volume of gas consumed, V_B, at the beginning of the next “ON” period. Measure the block temperature, T_C, and the energy consumed, E_C, or volume of gas consumed, V_C, at the end of that “ON” period. Measure the block temperature, T_D, and the energy consumed, E_D, or volume of gas consumed, V_D, at the beginning of the following “ON” period. Energy measurements for E_O, E_A, E_B, E_C and E_D should be expressed in watt-hours (kJ) for conventional electric ovens and volume measurements for V_A, V_B, V_C and V_D should be expressed in standard cubic feet (L) of gas for conventional gas ovens. For a gas oven that can be operated with or without forced convection, measure in watt-hours (kJ) any electrical energy consumed by an ignition device or other electrical components required for the operation of a conventional gas oven while heating the test block to T_O using the forced convection mode, (E_IO)₁, and without using the forced convection mode, (E_IO)₂. The energy consumed by a continuously operating clock that is an integral part of the timing or temperature control circuit and cannot be disconnected during the test may be subtracted from the oven test energy to obtain the test energy consumption, (E_O)₁ and (E_O)₂ or (E_IO)₁ and (E_IO)₂.

3.2.1.2  Energy consumption of self-cleaning operation. Measure the energy consumption, E_S, in watt-hours (kJ) of electricity or the volume of gas consumption, V_S, in standard cubic feet (L) during the self-cleaning test set forth in Section 3.1.1.1. For a gas oven, also measure in watt-hours (kJ) any electrical energy, E_IS, consumed by ignition devices or other electrical components required during the self-cleaning test. The energy consumed by a continuously operating clock that is an integral part of the timing or temperature control circuit and cannot be disconnected during the test may be subtracted from the self-cleaning test energy to obtain the energy consumption, E_S or E_IS

3.2.1.3  Gas consumption of continuously burning pilot lights. Measure the gas consumption of the pilot lights, V_OP, in standard cubic feet (L) of gas and the test duration, t_OP, in hours for the test set forth in Section 3.1.1.2. If a gas flow rate meter is used, measure the flow rate, Q_OP, in standard cubic feet per hour (L/h).

3.2.1.4  Clock power. If the conventional oven or conventional range includes an electric clock which is on continuously, and the power rating in watts (J/s) of this feature is not known, measure the clock power, P_CL, in watts (J/s.) The power rating or measurement of continuously operating clocks, that are an integral part of the timing or temperature control circuits and cannot be disconnected during testing, shall be multiplied by the applicable test period to calculate the clock energy consumption, in watt-hours (kJ), during a test. The energy consumed by the clock during the test may then be subtracted from the test energy to obtain the specified test energy consumption value.

3.2.2  Conventional surface unit test energy consumption. For the surface unit under test, measure the energy consumption, E_CT, in watt-hours (kJ) of electricity or the volume of gas consumption, V_CT, in standard cubic feet (L) of gas and the test block temperature, T_CT, at the end of the 15 minute (reduced input setting) test interval for the test specified in Section 3.1.2 and the total time, t_CT, in hours, that the unit is under test. Measure any electrical energy, E_IC, consumed by an ignition device of a gas heating element in watt-hours (kJ). The energy consumed by a continuously operating clock that is an integral part of the timing or temperature control circuit and cannot be disconnected during the test may be subtracted from the cooktop test energy to obtain the test energy consumption, E_CT or E_IC.

3.2.2.1  Gas consumption of continuously burning pilot lights. If the conventional gas cooking top under test has one or more continuously burning pilot lights, measure the gas consumed during the test by the pilot lights, V_CP, in standard cubic feet (L) of gas, and the test duration, t_CP, in hours as specified in Section 3.1.2.1. If a gas flow rate meter is used, measure the flow rate, Q_CP, in standard cubic feet per hour (L/h).

3.2.3  Microwave oven test energy consumption and power input. Measurements are to be made as specified in Section 4, Paragraphs 12.4 and 13 of IEC 705 and Amendment 2. Measure the electrical input energy, E_M, in watt-hours (kJ) consumed by the microwave oven during the test. Repeat the tests three times unless the power output value resulting from the second measurement is within 1.5% of the value obtained from the first measurement as stated in Section 4, Paragraphs 12.6 of IEC 705 Amendment 2. (See 10 CFR 430.22.)

3.3  Recorded values.

3.3.1  Record the test room temperature, T_R, at the start and end of each range, oven or cooktop test, as determined in Section 2.5.

3.3.2  Record measured test block weights W₁, W₂, and W₃ in pounds (kg).

3.3.3  Record the initial temperature, T₁, of the test block under test.

3.3.4  For a conventional oven with a thermostat which operates by cycling on and off, record the conventional oven test measurements T_A, E_A, T_B, E_B, T_C, E_C, T_D, and E_D for conventional electric ovens or T_A, V_A, T_B, V_B, T_C, V_C, T_D, and V_D for conventional gas ovens. If the thermostat controls the oven temperature without cycling on and off, record E_O. For a gas oven which also uses electrical energy for the ignition or operation of the oven, also record E_IO.

3.3.5  For a conventional oven that can be operated with or without forced convection and the oven thermostat controls the oven temperature without cycling on and off, measure the energy consumed with the forced convection mode, (E_O)₁, and without the forced convection mode, (E_O)₂. If the conventional oven operates with or without forced convection and the thermostat controls the oven temperature by cycling on and off, record the conventional oven test measurements T_A, E_A, T_B, E_B, T_C, E_C, T_D, and E_D for conventional electric ovens or T_A, V_A, T_B, V_B, T_C, V_C, T_D, and V_D for conventional gas ovens. For a gas oven that can be operated with or without forced convection, measure any electrical energy consumed by an ignition device or other electrical components used during the forced convection mode, (E_IO)₁, and without using the forced convection mode, (E_IO)₂.

3.3.6  Record the measured energy consumption, E_S, or gas consumption, V_S, and for a gas oven, any electrical energy, E_IS, for the test of the self-cleaning operation of a conventional oven.

3.3.7  Record the gas flow rate, Q_OP; or the gas consumption, V_OP, and the elapsed time, t_OP, that any continuously burning pilot lights of a conventional oven are under test.

3.3.8  Record the clock power measurement or rating, P_CL, in watts (J/s), except for microwave oven tests.

3.3.9  For the surface unit under test, record the electric energy consumption, E_CT, or the gas volume consumption, V_CT, the final test block temperature, T_CT, the total test time, t_CT. For a gas cooking top which uses electrical energy for ignition of the burners, also record E_IC.

3.3.10  Record the gas flow rate, Q_CP; or the gas consumption, V_CP, and the elapsed time, t_CP, that any continuously burning pilot lights of a conventional gas cooking top are under test.

3.3.11  Record the heating value, H_n, as determined in Section 2.2.2.2 for the natural gas supply.

3.3.12  Record the heating value, H_p, as determined in Section 2.2.2.3 for the propane supply.

3.3.13  Record the electrical input energy and power input, E_M and P_M, for the microwave oven test; the initial and final temperature, T₁ and T₂, of the test water load; the mass of the test container before filling with the test water load and the mass of the test water load, M_C and M_W respectively; and the measured room temperature, T₀; as determined in Section 3.2.3.

4. Calculation of Derived Results From Test Measurements

4.1  Conventional oven.

4.1.1  Test energy consumption. For a conventional oven with a thermostat which operates by cycling on and off, calculate the test energy consumption, E_O, expressed in watt-hours (kJ) for electric ovens and in Btu's (kJ) for gas ovens, and defined as:

for electric ovens, and,

For gas ovens

Where:

H = either H_n or H_p, the heating value of the gas used in the test as specified in Section 2.2.2.2 and Section 2.2.2.3, expressed in Btu's per standard cubic foot (kJ/L).

T_O = 234 °F (130 °C) plus the initial test block temperature.

and,

Where:

T_A = block temperature in °F (°C) at the end of the last “ON” period of the conventional oven before the test block reaches T_O.

T_B = block temperature in °F (°C) at the beginning of the “ON” period following the measurement of T_A.

T_C = block temperature in °F (°C) at the end of the “ON” period which starts with T_B.

T_D = block temperature in °F (°C) at the beginning of the “ON” period which follows the measurement of T_C.

E_A = electric energy consumed in Wh (kJ) at the end of the last “ON” period before the test block reaches T_O.

E_B = electric energy consumed in Wh (kJ) at the beginning of the “ON” period following the measurement of T_A.

E_C = electric energy consumed in Wh (kJ) at the end of the “ON” period which starts with T_B.

E_D = electric energy consumed in Wh (kJ) at the beginning of the “ON” period which follows the measurement of T_C.

V_A = volume of gas consumed in standard cubic feet (L) at the end of the last “ON” period before the test block reaches T_O.

V_B = volume of gas consumed in standard cubic feet (L) at the beginning of the “ON” period following the measurement of T_A.

V_C = volume of gas consumed in standard cubic feet (L) at the end of the “ON” period which starts with T_B.

V_D = volume of gas consumed in standard cubic feet (L) at the beginning of the “ON” period which follows the measurement of T_C.

The energy consumed by a continuously operating clock that cannot be disconnected during the test may be subtracted from the oven test energy to obtain the oven test energy consumption, E_O.

4.1.1.1  Average test energy consumption. If the conventional oven can be operated with or without forced convection, determine the average test energy consumption, E_O and E_IO, in watt-hours (kJ) for electric ovens and Btu's (kJ) for gas ovens using the following equations:

Where:

(E_O)₁=test energy consumption using the forced convection mode in watt-hours (kJ) for electric ovens and in Btu's (kJ) for gas ovens as measured in Section 3.2.1.1.

(E_O)₂=test energy consumption without using the forced convection mode in watt-hours (kJ) for electric ovens and in Btu's (kJ) for gas ovens as measured in Section 3.2.1.1.

(E_IO)₁=electrical energy consumption in watt-hours (kJ) of a gas oven in forced convection mode as measured in Section 3.2.1.1. (E_IO)₂=electrical energy consumption in watt-hours (kJ) of a gas oven without using the forced convection mode as measured in Section 3.2.1.1.

The energy consumed by a continuously operating clock that cannot be disconnected during the test may be subtracted from the oven test energy to obtain the average test energy consumption E_O and E_IO.

4.1.2  Conventional oven annual energy consumption.

4.1.2.1.  Annual cooking energy consumption.

4.1.2.1.1.  Annual primary energy consumption. Calculate the annual primary energy consumption for cooking, E_CO, expressed in kilowatt-hours (kJ) per year for electric ovens and in Btu's (kJ) per year for gas ovens, and defined as:

Where:

E _O=test energy consumption as measured in Section 3.2.1 or as calculated in Section 4.1.1 or Section 4.1.1.1.

K _e=3.412 Btu/Wh (3.6 kJ/Wh,) conversion factor of watt-hours to Btu's.

O _O=29.3 kWh (105,480 kJ) per year, annual useful cooking energy output of conventional electric oven.

W ₁=measured weight of test block in pounds (kg).

C _p=0.23 Btu/lb-°F (0.96 kJ/kg ÷ °C), specific heat of test block.

T _S=234 °F (130 °C), temperature rise of test block.

Where:

E_O=test energy consumption as measured in Section 3.2.1. or as calculated in Section 4.1.1 or Section 4.1.1.1.

O_O=88.8 kBtu (93,684 kJ) per year, annual useful cooking energy output of conventional gas oven.

W₁, C_p and T_S are the same as defined above.

4.1.2.1.2  Annual secondary energy consumption for cooking of gas ovens. Calculate the annual secondary energy consumption for cooking, E_SO, expressed in kilowatt-hours (kJ) per year and defined as:

Where:

E_IO=electrical test energy consumption as measured in Section 3.2.1 or as calculated in Section 4.1.1.1.

O_O=29.3 kWh (105,480 kJ) per year, annual useful cooking energy output.

K_e, W₁, C_p, and T_S are as defined in Section 4.1.2.1.1.

4.1.2.2  Annual energy consumption of any continuously burning pilot lights. Calculate the annual energy consumption of any continuously burning pilot lights, E_PO, expressed in Btu's (kJ) per year and defined as:

E_PO=Q_OP×H×(A−B),

or,

Where:

Q_OP=pilot gas flow rate in standard cubic feet per hour (L/h), as measured in Section 3.2.1.3.

V_OP=standard cubic feet (L) of gas consumed by any continuously burning pilot lights, as measured in Section 3.2.1.3.

t_OP=elapsed test time in hours for any continuously burning pilot lights tested, as measured in Section 3.2.1.3.

H=H_n or H_p, the heating value of the gas used in the test as specified in Section 2.2.2.2 and Section 2.2.2.3 in Btu's per standard cubic foot (kJ/L).

A=8,760, number of hours in a year.

B=300, number of hours per year any continuously burning pilot lights contribute to the heating of an oven for cooking food.

4.1.2.3  Annual conventional oven self-cleaning energy.

4.1.2.3.1  Annual primary energy consumption. Calculate the annual primary energy consumption for conventional oven self-cleaning operations, E_SC, expressed in kilowatt-hours (kJ) per year for electric ovens and in Btu's (kJ) for gas ovens, and defined as:

E_SC=E_S×S_e×K, for electric ovens,

Where:

E_S=energy consumption in watt-hours, as measured in Section 3.2.1.2.

S_e=4, average number of times a self-cleaning operation of a conventional electric oven is used per year.

K=0.001 kWh/Wh conversion factor for watt-hours to kilowatt-hours.

or

E_SC=V_S×H×S_g, for gas ovens,

Where:

V_S=gas consumption in standard cubic feet (L), as measured in Section 3.2.1.2.

H=H_n or H_p, the heating value of the gas used in the test as specified in Section 2.2.2.2 and Section 2.2.2.3 in Btu's per standard cubic foot (kJ/L).

S_g=4, average number of times a self-cleaning operation of a conventional gas oven is used per year.

The energy consumed by a continuously operating clock that cannot be disconnected during the self-cleaning test procedure may be subtracted from the test energy to obtain the test energy consumption, E_SC.

4.1.2.3.2  Annual secondary energy consumption for self-cleaning operation of gas ovens. Calculate the annual secondary energy consumption for self-cleaning operations of a gas oven, E_SS, expressed in kilowatt-hours (kJ) per year and defined as:

E_SS=E_IS × S_g × K,

Where:

E_IS=electrical energy consumed during the self-cleaning operation of a conventional gas oven, as measured in Section 3.2.1.2.

S_g=4, average number of times a self-cleaning operation of a conventional gas oven is used per year.

K=0.001 kWh/Wh conversion factor for watt-hours to kilowatt-hours.

4.1.2.4  Annual clock energy consumption. Calculate the annual energy consumption of any constantly operating electric clock, E_CL, expressed in kilowatt-hours (kJ) per year and defined as:

E_CL = P_CL × A × K,

Where:

P_CL=power rating of clock which is on continuously, in watts, as measured in Section 3.2.1.4.

A=8,760, number of hours in a year.

K=0.001 kWh/Wh conversion factor for watt-hours to kilowatt-hours.

4.1.2.5  Total annual energy consumption of a single conventional oven.

4.1.2.5.1  Conventional electric oven energy consumption. Calculate the total annual energy consumption of a conventional electric oven, E_AO, expressed in kilowatt-hours (kJ) per year and defined as:

E_AO=E_CO+E_SC+E_CL,

Where:

E_CO=annual primary cooking energy consumption as determined in Section 4.1.2.1.1.

E_SC=annual primary self-cleaning energy consumption as determined in Section 4.1.2.3.1.

E_CL=annual clock energy consumption as determined in Section 4.1.2.4.

4.1.2.5.2  Conventional gas oven energy consumption. Calculate the total annual gas energy consumption of a conventional gas oven, E_AOG, expressed in Btu's (kJ) per year and defined as:

E_AOG=E_CO+E_SC+E_PO,

Where:

E_CO=annual primary cooking energy consumption as determined in Section 4.1.2.1.1.

E_PO=annual pilot light energy consumption as determined in Section 4.1.2.2.

E_SC=annual primary self-cleaning energy consumption as determined in Section 4.1.2.3.1.

If the conventional gas oven uses electrical energy, calculate the total annual electrical energy consumption, E_AOE, expressed in kilowatt-hours (kJ) per year and defined as:

E_AOE=E_SO+E_SS+E_CL,

Where:

E_SO=annual secondary cooking energy consumption as determined in Section 4.1.2.1.2.

E_SS=annual secondary self-cleaning energy consumption as determined in Section 4.1.2.3.2.

E_CL=annual clock energy consumption as determined in Section 4.1.2.4.

4.1.2.6.  Total annual energy consumption of multiple conventional ovens. If the cooking appliance includes more than one conventional oven, calculate the total annual energy consumption of the conventional ovens using the following equations:

4.1.2.6.1  Conventional electric oven energy consumption. Calculate the total annual energy consumption, ETO, in kilowatt-hours (kJ) per year and defined as:

E_TO = E_ACO + E_ASC + E_CL,

Where:

is the average annual primary energy consumption for cooking,

and where:

n = number of conventional ovens in the basic model.

E_CO = annual primary energy consumption for cooking as determined in Section 4.1.2.1.1.

average annual self-cleaning energy consumption,

Where:

n = number of self-cleaning conventional ovens in the basic model.

E_SC = annual primary self-cleaning energy consumption as determined according to Section 4.1.2.3.1.

E_CL = clock energy consumption as determined according to Section 4.1.2.4.

4.1.2.6.2  Conventional gas oven energy consumption. Calculate the total annual gas energy consumption, E_TOG, in Btu's (kJ) per year and defined as:

E_TOG = E_ACO + E_ASC + E_TPO,

Where:

E_ACO = average annual primary energy consumption for cooking in Btu's (kJ) per year and is calculated as:

Where:

n = number of conventional ovens in the basic model.

E_CO = annual primary energy consumption for cooking as determined in Section 4.1.2.1.1.

and,

E_ASC = average annual self-cleaning energy consumption in Btu's (kJ) per year and is calculated as:

Where:

n = number of self-cleaning conventional ovens in the basic model.

E_SC = annual primary self-cleaning energy consumption as determined according to Section 4.1.2.3.1.

total energy consumption of any pilot lights,

Where:

E_PO = annual energy consumption of any continuously burning pilot lights determined according to Section 4.1.2.2.

n = number of pilot lights in the basic model.

If the oven also uses electrical energy, calculate the total annual electrical energy consumption, E_TOE, in kilowatt-hours (kJ) per year and defined as:

E_TOE = E_ASO + E_AAS + E_CL,

Where:

is the average annual secondary energy consumption for cooking,

Where:

n=number of conventional ovens in the basic model.

E_SO=annual secondary energy consumption for cooking of gas ovens as determined in Section 4.1.2.1.2.

is the average annual secondary self-cleaning energy consumption,

Where:

n=number of self-cleaning ovens in the basic model.

E_SS=annual secondary self-cleaning energy consumption of gas ovens as determined in Section 4.1.2.3.2.

E_CL=annual clock energy consumption as determined in Section 4.1.2.4.

4.1.3  Conventional oven cooking efficiency.

4.1.3.1  Single conventional oven. Calculate the conventional oven cooking efficiency, Eff_AO, using the following equations:

For electric ovens:

and,

For gas ovens:

Where:

W₁=measured weight of test block in pounds (kg).

C_p=0.23 Btu/lb-°F (0.96 kJ/kg÷ °C), specific heat of test block.

T_S=234 °F (130 °C), temperature rise of test block.

E_O=test energy consumption as measured in Section 3.2.1 or calculated in Section 4.1.1 or Section 4.1.1.1.

K_e=3.412 Btu/Wh (3.6 kJ/Wh), conversion factor for watt-hours to Btu's.

E_IO=electrical test energy consumption according to Section 3.2.1 or as calculated in Section 4.1.1.1.

4.1.3.2  Multiple conventional ovens. If the cooking appliance includes more than one conventional oven, calculate the cooking efficiency for all of the conventional ovens in the appliance, Eff_TO, using the following equation:

Where:

n=number of conventional ovens in the cooking appliance.

Eff_AO=cooking efficiency of each oven determined according to Section 4.1.3.1.

4.1.4  Conventional oven energy factor. Calculate the energy factor, or the ratio of useful cooking energy output to the total energy input, R_O, using the following equations:

For electric ovens,

Where:

O_O=29.3 kWh (105,480 kJ) per year, annual useful cooking energy output.

E_AO=total annual energy consumption for electric ovens as determined in Section 4.1.2.5.1.

For gas ovens:

Where:

O_O=88.8 kBtu (93,684 kJ) per year, annual useful cooking energy output.

E_AOG=total annual gas energy consumption for conventional gas ovens as determined in Section 4.1.2.5.2.

E_AOE=total annual electrical energy consumption for conventional gas ovens as determined in Section 4.1.2.5.2.

K_e=3,412 Btu/kWh (3,600 kJ/kWh), conversion factor for kilowatt-hours to Btu's.

4.2  Conventional cooking top

4.2.1  Conventional cooking top cooking efficiency

4.2.1.1  Electric surface unit cooking efficiency. Calculate the cooking efficiency, Eff_SU, of the electric surface unit under test, defined as:

Where:

W=measured weight of test block, W₂ or W₃, expressed in pounds (kg).

C_p=0.23 Btu/lb-°F (0.96 kJ/kg÷ °C), specific heat of test block.

T_SU=temperature rise of the test block: final test block temperature, T_CT, as determined in Section 3.2.2, minus the initial test block temperature, T_I, expressed in °F (°C) as determined in Section 2.7.5.

K_e=3.412 Btu/Wh (3.6 kJ/Wh), conversion factor of watt-hours to Btu's.

E_CT=measured energy consumption, as determined according to Section 3.2.2, expressed in watt-hours (kJ).

The energy consumed by a continuously operating clock that cannot be disconnected during the cooktop test may be subtracted from the energy consumption, E_CT, as determined in Section 3.2.2.

4.2.1.2  Gas surface unit cooking efficiency. Calculate the cooking efficiency, Eff_SU, of the gas surface unit under test, defined as:

Where:

W₃=measured weight of test block as measured in Section 3.3.2, expressed in pounds (kg).

C_p and T_SU are the same as defined in Section 4.2.1.1.

and,

E=[V_CT − V_CP×H] + (E_IC×K_e),

Where:

V_CT=total gas consumption in standard cubic feet (L) for the gas surface unit test as measured in Section 3.2.2.

E_IC=electrical energy consumed in watt-hours (kJ) by an ignition device of a gas surface unit as measured in Section 3.2.2.

K_e=3.412 Btu/Wh (3.6 kJ/Wh), conversion factor of watt-hours to Btu's.

H=either H_n or H_p, the heating value of the gas used in the test as specified in Section 2.2.2.2 and Section 2.2.2.3, expressed in Btu's per standard cubic foot (kJ/L) of gas.

V_CP=Q_CP×t_CT, pilot consumption, in standard cubic feet (L), during unit test,

Where:

t_CT=the elapsed test time as defined in Section 3.2.2.

and

(pilot flow in standard cubic feet per hour)

Where:

V_CP=any pilot lights gas consumption defined in Section 3.2.2.1.

t_CP=elapsed time of the cooking top pilot lights test as defined in Section 3.2.2.1.

4.2.1.3  Conventional cooking top cooking efficiency. Calculate the conventional cooking top cooking efficiency, Eff_CT, using the following equation:

Where:

n=number of surface units in the cooking top.

Eff_SU=the efficiency of each of the surface units, as determined according to Section 4.2.1.1 or Section 4.2.1.2.

4.2.2  Conventional cooking top annual energy consumption.

4.2.2.1  Conventional electric cooking top energy consumption. Calculate the annual energy consumption of an electric cooking top, E_CA, in kilowatt-hours (kJ) per year, defined as:

Where:

O_CT=173.1 kWh (623,160 kJ) per year, annual useful cooking energy output.

Eff_CT=conventional cooking top cooking efficiency as defined in Section 4.2.1.3.

4.2.2.2  Conventional gas cooking top

4.2.2.2.1  Annual cooking energy consumption. Calculate the annual energy consumption for cooking, E_CC, in Btu's (kJ) per year for a gas cooking top, defined as:

Where:

O_CT=527.6 kBtu (556,618 kJ) per year, annual useful cooking energy output.

Eff_CT=the gas cooking top efficiency as defined in Section 4.2.1.3.

4.2.2.2.2  Annual energy consumption of any continuously burning gas pilots. Calculate the annual energy consumption of any continuously burning gas pilot lights of the cooking top, E_PC, in Btu's (kJ) per year, defined as:

E_PC=Q_CP×A×H,

Where:

Q_CP=pilot light gas flow rate as measured in Section 3.2.2.1.

A=8,760 hours, the total number of hours in a year.

H=either H_n or H_p, the heating value of the gas used in the test as specified in Section 2.2.2.2. and Section 2.2.2.3, expressed in Btu's per standard cubic foot (kJ/L) of gas.

4.2.2.2.3  Total annual energy consumption of a conventional gas cooking top. Calculate the total annual energy consumption of a conventional gas cooking top, E_CA, in Btu's (kJ) per year, defined as:

E_CA=E_CC + E_PC,

Where:

E_CC=energy consumption for cooking as determined in Section 4.2.2.2.1.

E_PC=annual energy consumption of the pilot lights as determined in Section 4.2.2.2.2.

4.2.3  Conventional cooking top energy factor. Calculate the energy factor or ratio of useful cooking energy output for cooking to the total energy input, R_CT, as follows:

For an electric cooking top, the energy factor is the same as the cooking efficiency as determined according to Section 4.2.1.3.

For gas cooking tops,

Where:

O_CT=527.6 kBtu (556,618 kJ) per year, annual useful cooking energy output of cooking top.

E_CA=total annual energy consumption of cooking top determined according to Section 4.2.2.2.3.

4.3  Combined components. The annual energy consumption of a kitchen range, e.g. a cooktop and oven combined, shall be the sum of the annual energy consumption of each of its components. The annual energy consumption for other combinations of ovens, cooktops and microwaves will also be treated as the sum of the annual energy consumption of each of its components. The energy factor of a combined component is the sum of the annual useful cooking energy output of each component divided by the sum of the total annual energy consumption of each component.

4.4  Microwave oven.

4.4.1  Microwave oven test energy output. Calculate the microwave oven test energy output, E_T, in watt-hour's (kJ). The calculation is repeated two or three times as required in section 3.2.3. The average of the E_T's is used for a calculation in section 4.4.3. For calculations specified in units of energy [watt-hours (kJ)], use the equation below:

Where:

M_W=the measured mass of the test water load, in pounds (g).

M_C=the measured mass of the test container before filling with test water load, in pounds (g).

T₁=the initial test water load temperature, in °F (°C).

T₂=the final test water load temperature, in °F (°C).

T₀=the measured ambient room temperature, in °F (°C).

C_C=0.210 Btu/lb−°F (0.88 kJ/kg · °C), specific heat of test container.

C_p=1.0 Btu/lb−°F (4.187 kJ/kg · °C), specific heat of water.

K_e=3,412 Btu/kWh (3,600 kJ/kWh) conversion factor of kilowatt-hours to Btu's.

4.4.2  Microwave oven test power output. Calculate the microwave oven test power output, P_T, in watts (J/s) as specified in Section four, paragraph 12.5 of IEC 705 Amendment 2 See Section 430.22. The calculation is repeated for each test as required in section 3.2.3. The average of the two or three P_T's is used for calculations in section 4.4.4. (See 10 CFR 430.22)

4.4.3  Microwave oven annual energy consumption. Calculate the microwave oven annual energy consumption, E_mo, in KWh's per year, defined as:

Where:

E_M=the energy consumption as defined in Section 3.2.3.

O_M=79.8 kWh (287,280 kJ) per year, the microwave oven annual useful cooking energy output.

E_T=the test energy as calculated in Section 4.4.1.

4.4.4  Microwave oven cooking efficiency. Calculate the microwave oven cooking efficiency, Eff_MO, as specified in Section four, paragraph 14 of IEC 705.

4.4.5  Microwave oven energy factor. Calculate the energy factor or the ratio of the useful cooking energy output to total energy input on a yearly basis, R_MO, defined as:

Where:

O_M=79.8 kWh (287,280 kJ) per year, annual useful cooking energy output.

E_MO=annual total energy consumption as determined in Section 4.4.3.

[62 FR 51981, Oct. 3, 1997]

The provisions of this appendix J shall apply to products manufactured after April 13, 2001. The procedures and calculations in sections 3.3, 4.3, and 4.4 of this Appendix need not be performed to determine compliance with the energy conservation standards for clothes washers.

1. Definitions

1.1  Adaptive control system means a clothes washer control system, other than an adaptive water fill control system, which is capable of automatically adjusting washer operation or washing conditions based on characteristics of the clothes load placed in the clothes container, without allowing or requiring consumer intervention or actions. The automatic adjustments may, for example, include automatic selection, modification, or control of any of the following: wash water temperature, agitation or tumble cycle time, number of rinse cycles, and spin speed. The characteristics of the clothes load, which could trigger such adjustments, could, for example, consist of or be indicated by the presence of either soil, soap, suds, or any other additive laundering substitute or complementary product.

Note: Appendix J does not provide a means for determining the energy consumption of a clothes washer with an adaptive control system. Therefore, pursuant to 10 CFR 430.27, a waiver must be obtained to establish an acceptable test procedure for each such clothes washer.

1.2  Adaptive water fill control system means a clothes washer water fill control system which is capable of automatically adjusting the water fill level based on the size or weight of the clothes load placed in the clothes container, without allowing or requiring consumer intervention and/or actions.

1.3  Bone-dry means a condition of a load of test cloth which has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed and weighed before cool down, and then dried again for 10-minute periods until the final weight change of the load is 1 percent or less.

1.4  Clothes container means the compartment within the clothes washer that holds the clothes during operation of the machine.

1.5  Compact means a clothes washer which has a clothes container capacity of less than 1.6 ft³ (45 L).

1.6  Deep rinse cycle means a rinse cycle in which the clothes container is filled with water to a selected level and the clothes load is rinsed by agitating it or tumbling it through the water.

1.7  Front-loader clothes washer means a clothes washer which sequentially rotates or tumbles portions of the clothes load above the water level allowing the clothes load to fall freely back into the water. The principal axis of the clothes container is in a horizontal plane and the access to the clothes container is through the front of the machine.

1.8  Lockout means that at least one wash/rinse water temperature combination is not available in the normal cycle that is available in another cycle on the machine.

1.9  Make-up water means the amount of fresh water needed to supplement the amount of stored water pumped from the external laundry tub back into the clothes washer when the suds-return feature is activated in order to achieve the required water fill level in the clothes washer.

1.10  Modified energy factor means the quotient of the cubic foot (or liter) capacity of the clothes container divided by the total clothes washer energy consumption per cycle, with such energy consumption expressed as the sum of the machine electrical energy consumption, the hot water energy consumption, and the energy required for removal of the remaining moisture in the wash load.

1.11  Most energy intensive cycle means the non-normal cycle that uses the most energy for a given wash/rinse temperature combination.

1.12  Non-normal cycle means a cycle other than the normal cycle, but does not include any manually selected pre-wash, pre-soak, and extra-rinse option.

1.13  Nonwater-heating clothes washer means a clothes washer which does not have an internal water heating device to generate hot water.

1.14  Normal cycle means the cycle recommended by the manufacturer for washing cotton and/or linen clothes.

1.15  Sensor filled means a water fill control which automatically terminates the fill when the water reaches an appropriate level in the tub.

1.16  Spray rinse cycle means a rinse cycle in which water is sprayed onto the clothes load for a definite period of time without maintaining any specific water level in the clothes container.

1.17  Standard means a clothes washer which has a clothes container capacity of 1.6 ft³ (45 L) or greater.

1.18  Suds-return means a feature or option on a clothes washer which causes the stored wash water obtained by utilizing the suds-saver feature to be pumped from the external laundry tub back into the clothes washer.

1.19  Suds-saver means a feature or option on a clothes washer which allows the user to store used wash water in an external laundry tub for use with subsequent wash loads.

1.20  Temperature use factor means the percentage of the total number of washes a user would wash with a particular wash/rinse temperature setting.

1.21  Thermostatically controlled water valves means clothes washer controls that have the ability to sense and adjust the hot and cold supply water.

1.22  Time filled means a water fill control which uses a combination of water flow controls in conjunction with time to terminate the water fill cycle.

1.23  Top-loader-horizontal-axis clothes washer means a clothes washer which: rotates or tumbles portions of the clothes load above the water level allowing the clothes load to fall freely back into the water with the principal axis in a horizontal plane and has access to the clothes container through the top of the clothes washer.

1.24  Top-loader-vertical-axis clothes washer means a clothes washer that: flexes and oscillates the submerged clothes load through the water by means of mechanical agitation or other movement; has a clothes container with the principal axis in a vertical plane; and has access to the clothes container through the top of the clothes washer.

1.25  Water consumption factor means the quotient of the total weighted per-cycle water consumption divided by the capacity of the clothes washer.

1.26  Water-heating clothes washer means a clothes washer where some or all of the hot water for clothes washing is generated by a water heating device internal to the clothes washer.

2. Testing Conditions

2.1  Installation. Install the clothes washer in accordance with manufacturer's instructions.

2.2  Electrical energy supply. Maintain the electrical supply at the clothes washer terminal block within 2 percent of 120, 120/240 or 120/208Y volts as applicable to the particular terminal block wiring system as specified by the manufacturer. If the clothes washer has a dual voltage conversion capability, conduct the test at the highest voltage specified by the manufacturer.

2.3  Supply water. For nonwater-heating clothes washers not equipped with thermostatically controlled water valves, the temperature of the hot and cold water supply shall be maintained at 100 °F±10 °F (37.8 °C±5.5 °C). For nonwater-heating clothes washers equipped with thermostatically controlled water valves, the temperature of the hot water supply shall be maintained at 140 °F±5 °F (60.0 °C±2.8 °C) and the cold water supply shall be maintained at 60 °F±5 °F (15.6 °C±2.8 °C). For water-heating clothes washers, the temperature of the hot water supply shall be maintained at 140 °F±5 °F (60.0 °C±2.8 °C) and the cold water supply shall not exceed 60 °F (15.6 °C). Water meters shall be installed in both the hot and cold water lines to measure water consumption.

2.3.1  Supply water requirements for water and energy consumption testing. For nonwater-heating clothes washers not equipped with thermostatically controlled water valves, the temperature of the hot and cold water supply shall be maintained at 100° ±10 °F (37.8 °C ±5.5 °C). For nonwater-heating clothes washers equipped with thermostatically controlled water valves, the temperature of the hot water supply shall be maintained at 140 °F ±5 °F (60.0 °C ±2.8 °C) and the cold water supply shall be maintained at 60 °F ±5F° (15.6 °C ±2.8 °C). For water-heating clothes washers, the temperature of the hot water supply shall be maintained at 140 °F ±5 °F (60.0 °C ±2.8 °C) and the cold water supply shall not exceed 60 °F (15.6 °C). Water meters shall be installed in both the hot and cold water lines to measure water consumption.

2.3.2  Supply water requirements for remaining moisture content testing. For nonwater-heating clothes washers not equipped with thermostatically controlled water valves, the temperature of the hot water supply shall be maintained at 140 °F ±5 °F and the cold water supply shall be maintained at 60 °F ±5 °F. All other clothes washers shall be connected to water supply temperatures as stated in 2.3.1 of this appendix.

2.4  Water pressure. The static water pressure at the hot and cold water inlet connections of the machine shall be maintained during the test at 35 pounds per square inch gauge (psig)±2.5 psig (241.3 kPa±17.2 kPa). The static water pressure for a single water inlet connection shall be maintained during the test at 35 psig±2.5 psig (241.3 kPa±17.2 kPa). Water pressure gauges shall be installed in both the hot and cold water lines to measure water pressure.

2.5  Instrumentation. Perform all test measurements using the following instruments, as appropriate:

2.5.1  Weighing scales.

2.5.1.1  Weighing scale for test cloth. The scale shall have a resolution no larger than 0.2 oz (5.7 g) and a maximum error no greater than 0.3 percent of the measured value.

2.5.1.2  Weighing scale for clothes container capacity measurements. The scale should have a resolution no larger than 0.50 lbs (0.23 kg) and a maximum error no greater than 0.5 percent of the measured value.

2.5.2  Watt-hour meter. The watt-hour meter shall have a resolution no larger than 1 Wh (3.6 kJ) and a maximum error no greater than 2 percent of the measured value for any demand greater than 50 Wh (180.0 kJ).

2.5.3  Temperature measuring device. The device shall have an error no greater than ±1 °F (±0.6 °C) over the range being measured.

2.5.4  Water meter. The water meter shall have a resolution no larger than 0.1 gallons (0.4 liters) and a maximum error no greater than 2 percent for all water flow rates from 1 gal/min (3.8 L/min) to 5 gal/min (18.9 L/min).

2.5.5  Water pressure gauge. The water pressure gauge shall have a resolution no larger than 1 psig (6.9 kPa) and shall have an error no greater than 5 percent of any measured value over the range of 32.5 psig (224.1 kPa) to 37.5 psig (258.6 kPa).

2.6  Test cloths.

2.6.1  Energy test cloth. The energy test cloth shall be clean and consist of the following:

2.6.1.1  Pure finished bleached cloth, made with a momie or granite weave, which is 50 percent cotton and 50 percent polyester and weighs 5.75 oz/yd² (195.0 g/m² ) and has 65 ends on the warp and 57 picks on the fill.

2.6.1.2  Cloth material that is 24 in by 36 in (61.0 cm by 91.4 cm) and has been hemmed to 22 in by 34 in (55.9 cm by 86.4 cm) before washing. The maximum shrinkage after five washes shall not be more than four percent on the length and width.

2.6.1.3  The number of test runs on the same energy test cloth shall not exceed 60 test runs. All energy test cloth must be permanently marked identifying the lot number of the material. Mixed lots of material shall not be used for testing the clothes washers.

2.6.2  Energy Stuffer Cloth. The energy stuffer cloths shall be made from energy test cloth material and shall consist of pieces of material that are 12 inches by 12 inches (30.5 cm by 30.5 cm) and have been hemmed to 10 inches by 10 inches (25.4 cm by 25.4 cm) before washing. The maximum shrinkage after five washes shall not be more than four percent on the length and width. The number of test runs on the same energy suffer cloth shall not exceed 60 test runs. All energy stuffer cloth must be permanently marked identifying the lot number of the material. Mixed lots of material shall not be used for testing the clothes washers.

2.7  Composition of test loads.

2.7.1  Seven pound test load. The seven pound test load shall consist of bone-dry energy test cloths which weigh 7 lbs ±0.07 lbs (3.18 kg ±0.03 kg). Adjustments to the test load to achieve the proper weight can be made by the use of energy stuffer cloths.

2.7.2  Three pound test load. The three pound test load shall consist of bone-dry energy test cloths which weigh 3 lbs ±0.03 lbs (1.36 kg ±0.014 kg). Adjustments to the test load to achieve the proper weight can be made by the use of energy stuffer cloths.

2.8  Use of test loads.

2.8.1  For a standard size clothes washer, a seven pound load, as described in section 2.7.1, shall be used to test the maximum water fill and a three pound test load, as described in section 2.7.2, shall be used to test the minimum water fill.

2.8.2  For a compact size clothes washer, a three pound test load as described in section 2.7.2 shall be used to test the maximum and minimum water fill levels.

2.8.3  A vertical-axis clothes washer without adaptive water fill control system also shall be tested without a test load for purposes of calculating the energy factor.

2.8.4  The test load sizes to be used to measure remaining moisture content (RMC) are specified in section 3.3.2.

2.8.5  Load the energy test cloths by grasping them in the center, shaking them to hang loosely and then dropping them into the clothes container prior to activating the clothes washer.

2.9  Preconditioning. If the clothes washer has not been filled with water in the preceding 96 hours, pre-condition it by running it through a cold rinse cycle and then draining it to ensure that the hose, pump, and sump are filled with water.

2.10  Wash time (period of agitation or tumble) setting. If the maximum available wash time in the normal cycle is greater than 9.75 minutes, the wash time shall be not less than 9.75 minutes. If the maximum available wash time in the normal cycle is less than 9.75 minutes, the wash time shall be the maximum available wash time.

2.11  Agitation speed and spin speed settings. Where controls are provided for agitation speed and spin speed selections, set them as follows:

2.11.1  For energy and water consumption tests, set at the normal cycle settings. If settings at the normal cycle are not offered, set the control settings to the maximum speed permitted on the clothes washer.

2.11.2  For remaining moisture content tests, see section 3.3.

3. Test Measurements

3.1  Clothes container capacity. Measure the entire volume which a dry clothes load could occupy within the clothes container during washer operation according to sections 3.1.1 through 3.1.5.

3.1.1  Place the clothes washer in such a position that the uppermost edge of the clothes container opening is leveled horizontally, so that the container will hold the maximum amount of water.

3.1.2  Line the inside of the clothes container with 2 mil (0.051 mm) plastic sheet. All clothes washer components which occupy space within the clothes container and which are recommended for use with the energy test cycle shall be in place and shall be lined with 2 mil (0.051 mm) plastic sheet to prevent water from entering any void space.

3.1.3  Record the total weight of the machine before adding water.

3.1.4  Fill the clothes container manually with either 60 °F ±5 °F (15.6 °C ±2.8 °C) or 100 °F ±10 °F (37.8 °C ±5.5 °C) water to its uppermost edge. Measure and record the weight of water, W, in pounds.

3.1.5  The clothes container capacity is calculated as follows:

C=W/d.

where:

C=Capacity in cubic feet (or liters).

W=Mass of water in pounds (or kilograms).

d=Density of water (62.0 lbs/ft³ for 100 °F (993 kg/m³ for 37.8 °C) or 62.3 lbs/ft³ for 60 °F (998 kg/m³ for 15.6 °C)).

3.2  Test cycle. Establish the test conditions set forth in section 2 of this Appendix.

3.2.1  A clothes washer that has infinite temperature selections shall be tested at the following temperature settings: hottest setting available on the machine, hot (a minimum of 140 °F (60.0 °C) and a maximum of 145 °F (62.8 °C)), warm (a minimum of 100 °F (37.8 °C) and a maximum of 105 °F (40.6 °C)), and coldest setting available on the machine. These temperatures must be confirmed by measurement using a temperature measuring device. If the measured final water temperature is not within the specified range, stop testing, adjust the temperature selector accordingly, and repeat the procedure.

3.2.2  Clothes washers with adaptive water fill control system and/or unique temperature selections.

3.2.2.1  Clothes washers with adaptive water fill control system. When testing a clothes washer that has adaptive water fill control, the maximum and the minimum test loads as specified in 2.8.1 and 2.8.2 shall be used. The amount of water fill shall be determined by the control system. If the clothes washer provides consumer selection of variable water fill amounts for the adaptive water fill control system, two complete sets of tests shall be conducted. The first set of tests shall be conducted with the adaptive water fill control system set in the setting that will use the greatest amount of energy. The second set of tests shall be conducted with the adaptive water fill control system set in the setting that will use the smallest amount of energy. Then, the results from these two tests shall be averaged to determine the adaptive water fill energy consumption value. If a clothes washer with an adaptive water fill control system allows consumer selection of manual controls as an alternative, both the manual and adaptive modes shall be tested and the energy consumption values, E_T, M_E, and D_E (if desired), calculated in section 4 for each mode, shall be averaged between the manual and adaptive modes.

3.2.2.2  Clothes washers with multiple warm wash temperature combination selections.

3.2.2.2.1  If a clothes washer's temperature combination selections are such that the temperature of each warm wash setting that is above the mean warm wash temperature (the mean temperature of the coldest and warmest warm settings) is matched by a warm wash setting that is an equal distance below the mean, then the energy test shall be conducted at the mean warm wash temperature if such a selection is provided, or if there is no position on the control that permits selection of the mean temperature, the energy test shall be conducted with the temperature selection set at the next hotter temperature setting that is available above the mean.

3.2.2.2.2  If the multiple warm wash temperature combination selections do not meet criteria in section 3.2.2.2.1, the energy test shall be conducted with the temperature selection set at the warm wash temperature setting that gives the next higher water temperature than the mean temperature of the coldest and warmest warm settings.

3.2.2.3  Clothes washers with multiple temperature settings within a temperature combination selection. When a clothes washer is provided with a secondary control that can modify the wash or rinse temperature within a temperature combination selection, the secondary control shall be set to provide the hottest wash temperature available and the hottest rinse temperature available. For instance, when the temperature combination selection is set for the middle warm wash temperature and a secondary control exists which allows this temperature to be increased or decreased, the secondary control shall be set to provide the hottest warm wash temperature available for the middle warm wash setting.

3.2.3  Clothes washers that do not lockout any wash/rinse temperature combinations in the normal cycle. Test in the normal cycle all temperature combination selections that are required to be tested.

3.2.3.1  Hot water consumption, cold water consumption, and electrical energy consumption at maximum fill. Set the water level selector at maximum fill available on the clothes washer, if manually controlled, and insert the appropriate test load, if applicable. Activate the normal cycle of the clothes washer and also any suds-saver switch.

3.2.3.1.1  For automatic clothes washers, set the wash/rinse temperature selector to the hottest temperature combination setting. For semi-automatic clothes washers, open the hot water faucet valve completely and close the cold water faucet valve completely to achieve the hottest temperature combination setting.

3.2.3.1.2  Measure the electrical energy consumption of the clothes washer for the complete cycle.

3.2.3.1.3  Measure the respective number of gallons (or liters) of hot and cold water used to fill the tub for the wash cycle.

3.2.3.1.4  Measure the respective number of gallons (or liters) of hot and cold water used for all deep rinse cycles.

3.2.3.1.5  Measure the respective gallons (or liters) of hot and cold water used for all spray rinse cycles.

3.2.3.1.6  For non-water-heating automatic clothes washers repeat sections 3.2.3.1.3 through 3.2.3.1.5 for each of the other wash/rinse temperature selections available that uses heated water and is required to be tested. For water-heating clothes washers, repeat sections 3.2.3.1.2 through 3.2.3.1.5 for each of the other wash/rinse temperature selections available that uses heated water and is required to be tested. (When calculating water consumption under section 4.3 for any machine covered by the previous two sentences, also test the cold wash/cold rinse selection.) For semi-automatic clothes washers, repeat sections 3.2.3.1.3 through 3.2.3.1.5 for the other wash/rinse temperature settings in section 6 with the following water faucet valve adjustments:

3.2.3.1.7  If the clothes washer is equipped with a suds-saver cycle, repeat sections 3.2.3.1.2 to 3.2.3.1.5 with suds-saver switch set to suds return for the Warm/Cold temperature setting.

3.2.3.2  Hot water consumption, cold water consumption, and electrical energy consumption with the water level selector at minimum fill. Set the water level selector at minimum fill, if manually controlled, and insert the appropriate test load, if applicable. Activate the normal cycle of the clothes washer and also any suds-saver switch. Repeat sections 3.2.3.1.1 through 3.2.3.1.7.

3.2.3.3  Hot and cold water consumption for clothes washers that incorporate a partial fill during the rinse cycle. For clothes washers that incorporate a partial fill during the rinse cycle, activate any suds-saver switch and operate the clothes washer for the complete normal cycle at both the maximum water fill level and the minimum water fill level for each of the wash/rinse temperature selections available. Measure the respective hot and cold water consumed during the complete normal cycle.

3.2.4  Clothes washers that lockout any wash/rinse temperature combinations in the normal cycle. In addition to the normal cycle tests in section 3.2.3, perform the following tests on non-normal cycles for each wash/rinse temperature combination selection that is locked out in the normal cycle.

3.2.4.1  Set the cycle selector to a non-normal cycle which has the wash/rinse temperature combination selection that is locked out. Set the water level selector at maximum fill and insert the appropriate test load, if applicable. Activate the cycle of the clothes washer and also any suds-saver switch. Set the wash/rinse temperature selector to the temperature combination setting that is locked out in the normal cycle and repeat sections 3.2.3.1.2 through 3.2.3.1.5.

3.2.4.2  Repeat section 3.2.4.1 under the same temperature combination setting for all other untested non-normal cycles on the machine that have the wash/rinse temperature combination selection that is locked out.

3.2.4.3  Total the measured hot water consumption of the wash, deep rinse, and spray rinse of each non-normal cycle tested in sections 3.2.4.1 through 3.2.4.2 and compare the total for each cycle. The cycle that has the highest hot water consumption shall be the most energy intensive cycle for that particular wash/rinse temperature combination setting.

3.2.4.4  Set the water level selector at minimum fill and insert the appropriate test load, if applicable. Activate the most energy intensive cycle, as determined in section 3.2.4.3, of the clothes washer and also any suds-saver switch. Repeat tests as described in section 3.2.4.1.

3.3    Remaining Moisture Content (RMC).

3.3.1  The wash temperature shall be the same as the rinse temperature for all testing. Cold rinse is the coldest rinse temperature available on the machine. Warm rinse is the hottest rinse temperature available on the machine.

3.3.2  Determine the test load as shown in the following table:

3.3.3  For clothes washers with cold rinse only.

3.3.3.1  Record the actual bone dry weight of the test load (WI), then place the test load in the clothes washer.

3.3.3.2  Set water level selector to maximum fill.

3.3.3.3  Run the normal cycle.

3.3.3.4  Record the weight of the test load immediately after completion of the normal cycle (WC).

3.3.3.5  Calculate the remaining moisture content of the test load, RMC, expressed as a percentage and defined as:

RMC=[(WC−WI)/WI]×100%

3.3.4  For clothes washers with cold and warm rinse options.

3.3.4.1  Complete steps 3.3.3.1 through 3.3.3.4 for the cold rinse. Calculate the remaining moisture content of the test load for cold rinse, RMC_COLD, expressed as a percentage and defined as:

RMC_COLD=[(WC−WI)/WI]×100%

3.3.4.2  Complete steps 3.3.3.1 through 3.3.3.4 for the warm rinse. Calculate the remaining moisture content of the test load for warm rinse, RMC_WARM, expressed as a percentage and defined as:

RMC_WARM=[(WC−WI)/WI]×100%

3.3.4.3  Calculate the remaining moisture content of the test load, RMC, expressed as a percentage and defined as:

RMC=0.73×RMC_COLD+0.27×RMC_WARM

3.3.5  Clothes washers which have options that result in different RMC values, such as multiple selection of spin speeds or spin times that are available in the normal cycle, shall be tested at the maximum and minimum settings of the available options, excluding any “no spin” (zero spin speed) settings, in accordance with requirements in 3.3.3 or 3.3.4. The calculated RMC_{max extraction} and RMC_{min extraction} at the maximum and minimum settings, respectively, shall be combined as follows and the final RMC to be used in section 4.2 shall be:

RMC=0.75×RMC_{max extraction}+0.25×RMC_{min extraction}

3.4  Data recording. Record for each test cycle in sections 3.2.1 through 3.3.5.

3.4.1  For non-water-heating clothes washers, record the kilowatt-hours of electrical energy, M_E, consumed during the test to operate the clothes washer in section 3.2.3.1.2. For water-heating clothes washers record the kilowatt-hours of electrical energy, Eh_i consumed at maximum fill in sections 3.2.3.1.2 and 3.2.3.1.6, and Eh_j consumed at minimum fill in section 3.2.3.2.

3.4.2  Record the individual gallons (or liters) of hot and cold water consumption, Vh_i and Vc_i, measured at maximum fill level for each wash/rinse temperature combination setting tested in section 3.2.3, or in both 3.2.3 and 3.2.4, excluding any fresh make-up water required to complete the fill during a suds-return cycle.

3.4.3  Record the individual gallons (or liters) of hot and cold water consumption, Vh_j and Vc_j, measured at minimum fill level for each wash/rinse temperature combination setting tested in section 3.2.3, or in both 3.2.3 and 3.2.4, excluding any fresh make-up water required to complete the fill during a suds-return cycle.

3.4.4  Record the individual gallons (or liters) of hot and cold water, Sh_H and Sc_H, measured at maximum fill for the suds-return cycle.

3.4.5  Record the individual gallons (or liters) of hot and cold water, Sh_L and Sc_L, measured at minimum fill for the suds-return cycle.

3.4.6  Data recording requirements for RMC tests are listed in sections 3.3.3 through 3.3.5.

4. Calculation of Derived Results From Test Measurements

4.1  Energy consumption.

4.1.1  Per-cycle temperature-weighted hot water consumption for maximum and minimum water fill levels. Calculate for the cycle under test the per-cycle temperature weighted hot water consumption for the maximum water fill level, Vh_max, and for the minimum water fill level, Vh_min, expressed in gallons per cycle (or liters per cycle) and defined as:

where:

Vh_i=reported hot water consumption in gallons per cycle (or liters per cycle) at maximum fill for each wash/rinse temperature combination setting, as provided in section 3.4.2. If a clothes washer is equipped with two or more different wash/rinse temperature selections that have the same basic temperature combination selection label (for example, one of them has its water temperature controlled by thermostatically controlled valves and the other one does not), then the largest Vh_i shall be used for this calculation. If a clothes washer has lockout(s), there will be “Vh_i's” for wash/rinse temperature combination settings available in the normal cycle and “Vh_i's” for wash/rinse temperature combination settings in the most energy intensive cycle.

Vh_j=reported hot water consumption in gallons per cycle (or liters per cycle) at minimum fill for each wash/rinse temperature combination setting, as provided in section 3.4.3. If a clothes washer is equipped with two or more different wash/rinse temperature selections that have the same basic temperature combination selection label (for example, one of them has its water temperature controlled by thermostatically controlled valves and the other one does not), then the largest Vh_j shall be used for the calculation. If a clothes washer has lockouts, there will be “Vh_j's” for wash/rinse temperature combination settings available in the normal cycle and “Vh_j's” for wash/rinse temperature combination settings in the most energy intensive cycle.

L=lockout factor to be applied to the reported hot water consumption. For wash/rinse temperature combination settings that are not locked out in the normal cycle, L=1. For each wash/rinse temperature combination setting that is locked out in the normal cycle, L=0.32 in the normal cycle and L=0.68, in the most energy intensive cycle.

TUF_i=applicable temperature use factor in section 5 or 6.

TUF_j=applicable temperature use factor in section 5 or 6.

n=number of wash/rinse temperature combination settings available to the user for the clothes washer under test. For clothes washers that lockout temperature selections in the normal cycle, n=the number of wash/rinse temperature combination settings on the washers plus the number of wash/rinse temperature combination settings that lockout the temperature selections in the normal cycle.

TUF_w=temperature use factor for warm wash setting.

For clothes washers equipped with the suds-saver feature:

X₁=frequency of use without the suds-saver feature=0.86.

X₂=frequency of use with the suds-saver feature=0.14.

Sh_H=fresh make-up water measured during suds-return cycle at maximum water fill level.

Sh_L=fresh hot make-up water measured during suds-return cycle at minimum water fill level.

For clothes washers not equipped with the suds-saver feature:

X₁=1.0

X₂=0.0

4.1.2  Total per-cycle hot water energy consumption for maximum and minimum water fill levels. Calculate the total per-cycle hot water energy consumption for the maximum water fill level, E_max and for the minimum water fill level, E_min, expressed in kilowatt-hours per cycle and defined as:

E_max=[Vh_max×T×K×MF]

E_min=[Vh_min×T×K×MF]

where:

T=temperature rise=90 °F (50 °C).

K=water specific heat=0.00240 kWh/(gal– °F) [0.00114kWh/(L– °C)].

Vh_max=as defined in section 4.1.1.

Vh_min=as defined in section 4.1.1.

MF=multiplying factor to account for absence of test load=0.94 for top-loader vertical axis clothes washers that are sensor filled, 1.0 for all other clothes washers.

4.1.3  Total weighted per-cycle hot water energy consumption expressed in kilowatt-hours. Calculate the total weighted per cycle hot water energy consumption, E_T, expressed in kilowatt-hours per cycle and defined as:

E_T=[E_max×F_max]+[E_min×F_min]

where:

F_max=usage fill factor=0.72.

F_min=usage fill factor=0.28.

E_max=as defined in section 4.1.2.

E_min=as defined in section 4.1.2.

4.1.4  Per-cycle water energy consumption using gas-heated or oil-heated water. Calculate for the normal cycle the per-cycle energy consumption, E_TG, using gas-heated or oil-heated water, expressed in Btu per cycle (or megajoules per cycle) and defined as:

where:

e=nominal gas or oil water heater efficiency=0.75.

E_T=as defined in section 4.1.3.

4.1.5  Per-cycle machine electrical energy consumption.

4.1.5.1  Non-water-heating clothes washers. The electrical energy value recorded for the maximum fill in section 3.4.1 is the per-cycle machine electrical energy consumption, M_E, expressed in kilowatt-hours per cycle.

4.1.5.2  Water-heating clothes washers.

4.1.5.2.1  Calculate for the cycle under test the per-cycle temperature weighted electrical energy consumption for the maximum water fill level, Eh_max, and for the minimum water fill level, Eh_min, expressed in kilowatt-hours per cycle and defined as:

where:

Eh_i=reported electrical energy consumption in kilowatt-hours per cycle at maximum fill for each wash/cycle temperature combination setting, as provided in section 3.4.1.

TUF_i=applicable temperature use factor in section 5 or 6.

n=number of wash/rinse temperature combination settings available to the user for the clothes washer under test.

and

where:

Eh_j=reported electrical energy consumption in kilowatt-hours per cycle at minimum fill for each wash/rinse temperature combination setting, as provided in section 3.4.1.

TUF_j=applicable temperature use factor in section 5 or 6.

n=as defined above in this section.

4.1.5.2.2  Weighted per-cycle machine electrical energy consumption. Calculate the weighted per cycle machine energy consumption, M_E, expressed in kilowatt-hours per cycle and defined as:

M_E=[Eh_max×F_max]+[Eh_min×F_min]

where:

F_max=as defined in section 4.1.3.

F_min=as defined in section 4.1.3.

Eh_max=as defined in section 4.1.5.2.1.

Eh_min=as defined in section 4.1.5.2.1

4.1.6  Total per-cycle energy consumption when electrically heated water is used. Calculate for the normal cycle the total per-cycle energy consumption, E_TE, using electrically heated water, expressed in kilowatt-hours per cycle and defined as:

E_TE=E_T+M_E

where:

E_T=as defined in section 4.1.3.

M_E=as defined in section 4.1.5.1 or 4.1.5.2.2.

4.2  Per-cycle energy consumption for removal of RMC. Calculate the amount of energy per cycle required to remove RMC. Such amount is D_E, expressed in kilowatt-hours per cycle and defined as:

D_E=(LAF)×(test load weight)×(RMC−4%)×(DEF)×(DUF)

where:

LAF=load adjustment factor=0.52.

Test load weight=as shown in test load table in 3.3.2 expressed in lbs/cycle.

RMC=as defined in 3.3.3.5, 3.3.4.3, or 3.3.5.

DEF=nominal energy required for a clothes dryer to remove moisture from clothes=0.5 kWh/lb (1.1 kWh/kg).

DUF=dryer usage factor, percentage of washer loads dried in a clothes dryer=0.84.

4.3  Water consumption.

4.3.1  Per-cycle temperature-weighted water consumption for maximum and minimum water fill levels. To determine these amounts, calculate for the cycle under test the per-cycle temperature-weighted total water consumption for the maximum water fill level, Q_max, and for the minimum water fill level, Q_min, expressed in gallons per cycle (or liters per cycle) and defined as:

where:

Vh_i=hot water consumption in gallons per-cycle at maximum fill for each wash/rinse temperature combination setting, as provided in section 3.4.2.

Vc_i=total cold water consumption in gallons per-cycle at maximum fill for each wash/rinse temperature combination setting, cold wash/cold rinse cycle, as provided in section 3.4.2.

TUF_i=applicable temperature use factor in section 5 or 6.

n=number of wash/rinse temperature combination settings available to the user for the clothes washer under test.

TUF_w=temperature use factor for warm wash setting.

For clothes washers equipped with suds-saver feature:

X₁=frequency of use without suds-saver feature=0.86

X₂=frequency of use with suds-saver feature=0.14

Sh_H=fresh hot water make-up measured during suds-return cycle at maximum water fill level.

Sc_H=fresh cold water make-up measured during suds-return cycle at maximum water fill level.

For clothes washers not equipped with suds-saver feature:

X₁=1.0

X₂=0.0

and

where:

Vh_j=hot water consumption in gallons per cycle (or liters per cycle) at minimum fill for each wash/rinse temperature combination setting, as provided in section 3.4.3.

Vc_j=cold water consumption in gallons per cycle (or liters per cycle) at minimum fill for each wash/rinse temperature combination setting, cold wash/cold rinse cycle, as provided in section 3.4.3.

TUF_j=applicable temperature use factor in section 5 or 6.

Sh_L=fresh hot make-up water measured during suds-return cycle at minimum water fill level.

Sc_L=fresh cold make-up water measured during suds-return cycle at minimum water fill level.

n=as defined above in this section.

TUF_w=as defined above in this section.

X₁=as defined above in this section.

X₂=as defined above in this section.

4.3.2  Total weighted per-cycle water consumption. To determine this amount, calculate the total weighted per cycle water consumption, Q_T, expressed in gallons per cycle (or liters per cycle) and defined as:

Q_T=[Q_max×F_max]+[Q_min×F_min]

where:

F_max=as defined in section 4.1.3.

F_min=as defined in section 4.1.3.

Q_max=as defined in section 4.3.1.

Q_min=as defined in section 4.3.1.

4.3.3  Water consumption factor. The following calculates the water consumption factor, WCF, expressed in gallon per cycle per cubic foot (or liter per cycle per liter):

WCF=Q_T/C

where:

C=as defined in section 3.1.5.

Q_T=as defined in section 4.3.2.

4.4  Modified energy factor. The following calculates the modified energy factor, MEF, expressed in cubic feet per kilowatt-hours per cycle (or liters per kilowatt-hours per cycle):

where:

C=as defined in section 3.1.5.

M_E=as defined in section 4.1.5.1 or 4.1.5.2.2.

E_T=as defined in section 4.1.3.

D_E=as defined in section 4.2.

4.5  Energy factor. Calculate the energy factor, EF, expressed in cubic feet per kilowatt-hours per cycle (or liters per kilowatt-hours per cycle), as:

where:

C=as defined in section 3.1.5.

M_E=as defined in section 4.1.5.1 or 4.1.5.2.2.

E_T=as defined in section 4.1.3.

5. Applicable Temperature Use Factors for Determining Hot Water Usage for Various Wash/Rinse Temperature Selections for All Automatic Clothes Washers

5.1  Clothes washers with discrete temperature selections.

5.1.1  Five-temperature selection (n=5).

5.1.2  Four-temperature selection (n=4).

5.1.3  Three-temperature selection (n=3).

5.1.4  Two-temperature selection (n=2).

5.1.5  One-temperature selection (n=1).

5.2  Clothes washers with infinite temperature selections.

6. Applicable Temperature Use Factors for Determining Hot Water Usage for Various Wash/Rinse Temperature Settings for All Semi-Automatic, Non-Water-Heating, Clothes Washers

6.1  Six-temperature settings (n=6).

7. Waivers and Field Testing

7.1  Waivers and Field Testing for Non-conventional Clothes Washers. Manufacturers of non-conventional clothes washers, such as clothes washers with adaptive control systems, must submit a petition for waiver pursuant to 10 CFR 430.27 to establish an acceptable test procedure for that clothes washer. For these and other clothes washers that have controls or systems such that the DOE test procedures yield results that are so unrepresentative of the clothes washer's true energy consumption characteristics as to provide materially inaccurate comparative data, field testing may be appropriate for establishing an acceptable test procedure. The following are guidelines for field testing which may be used by manufacturers in support of petitions for waiver. These guidelines are not mandatory and the Department may determine that they do not apply to a particular model. Depending upon a manufacturer's approach for conducting field testing, additional data may be required. Manufacturers are encouraged to communicate with the Department prior to the commencement of field tests which may be used to support a petition for waiver. Section 7.3 provides an example of field testing for a clothes washer with an adaptive water fill control system. Other features, such as the use of various spin speed selections, could be the subject of field tests.

7.2  Non-conventional Wash System Energy Consumption Test. The field test may consist of a minimum of 10 of the nonconventional clothes washers (“test clothes washers”) and 10 clothes washers already being distributed in commerce (“base clothes washers”). The tests should include a minimum of 50 normal test cycles per clothes washer. The test clothes washers and base clothes washers should be identical in construction except for the controls or systems being tested. Equal numbers of both the test clothes washer and the base clothes washer should be tested simultaneously in comparable settings to minimize seasonal and/or consumer laundering conditions and/or variations. The clothes washers should be monitored in such a way as to accurately record the total energy consumption per cycle. At a minimum, the following should be measured and recorded throughout the test period for each clothes washer: Hot water usage in gallons (or liters), electrical energy usage in kilowatt-hours, and the cycles of usage. The field test results would be used to determine the best method to correlate the rating of the test clothes washer to the rating of the base clothes washer. If the base clothes washer is rated at A kWh per year, but field tests at B kWh per year, and the test clothes washer field tests at D kWh per year, the test unit would be rated as follows:

A×(D/B)=G kWh per year

7.3  Adaptive water fill control system field test. Section 3.2.2.1 defines the test method for measuring energy consumption for clothes washers which incorporate control systems having both adaptive and alternate manual selections. Energy consumption calculated by the method defined in section 3.2.2.1 assumes the adaptive cycle will be used 50 percent of the time. This section can be used to develop field test data in support of a petition for waiver when it is believed that the adaptive cycle will be used more than 50 percent of the time. The field test sample size should be a minimum of 10 test clothes washers. The test clothes washers should be totally representative of the design, construction, and control system that will be placed in commerce. The duration of field testing in the user's house should be a minimum of 50 normal test cycles, for each unit. No special instructions as to cycle selection or product usage should be given to the field test participants, other than inclusion of the product literature pack which should be shipped with all units, and instructions regarding filling out data collection forms, use of data collection equipment, or basic procedural methods. Prior to the test clothes washers being installed in the field test locations, baseline data should be developed for all field test units by conducting laboratory tests as defined by section 1 through section 6 of these test procedures to determine the energy consumption values. The following data should be measured and recorded for each wash load during the test period: wash cycle selected, the mode of the clothes washer (adaptive or manual), clothes load dry weight (measured after the clothes washer and clothes dryer cycles are completed) in pounds, and type of articles in the clothes load (i.e., cottons, linens, permanent press, etc.). The wash loads used in calculating the in-home percentage split between adaptive and manual cycle usage should be only those wash loads which conform to the definition of the normal test cycle.

Calculate:

T=The total number of normal test cycles run during the field test

T_a=The total number of adaptive control normal test cycles

T_m=The total number of manual control normal test cycles

The percentage weighting factors:

P_a=(T_a/T) × 100 (the percentage weighting for adaptive control selection)

P_m=(T_m/T) × 100 (the percentage weighting for manual control selection)

Energy consumption values, E_T, M_E, and D_E (if desired) calculated in section 4 for the manual and adaptive modes, should be combined using P_a and P_m as the weighting factors.

8. Sunset

The provisions of this appendix J expire on December 31, 2003.

[62 FR 45501, Aug. 27, 1997, as amended at 66 FR 3330, Jan. 12, 2001; 66 FR 8745, Feb. 2, 2001]

The provisions of this appendix J1 shall apply to products manufactured beginning January 1, 2004.

1. Definitions and Symbols

1.1  Adaptive control system means a clothes washer control system, other than an adaptive water fill control system, which is capable of automatically adjusting washer operation or washing conditions based on characteristics of the clothes load placed in the clothes container, without allowing or requiring consumer intervention or actions. The automatic adjustments may, for example, include automatic selection, modification, or control of any of the following: wash water temperature, agitation or tumble cycle time, number of rinse cycles, and spin speed. The characteristics of the clothes load, which could trigger such adjustments, could, for example, consist of or be indicated by the presence of either soil, soap, suds, or any other additive laundering substitute or complementary product.

Note: Appendix J1 does not provide a means for determining the energy consumption of a clothes washer with an adaptive control system. Therefore, pursuant to 10 CFR 430.27, a waiver must be obtained to establish an acceptable test procedure for each such clothes washer.

1.2  Adaptive water fill control system means a clothes washer water fill control system which is capable of automatically adjusting the water fill level based on the size or weight of the clothes load placed in the clothes container, without allowing or requiring consumer intervention or actions.

1.3  Bone-dry means a condition of a load of test cloth which has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed and weighed before cool down, and then dried again for 10 minute periods until the final weight change of the load is 1 percent or less.

1.4  Clothes container means the compartment within the clothes washer that holds the clothes during the operation of the machine.

1.5  Compact means a clothes washer which has a clothes container capacity of less than 1.6 ft³ (45 L).

1.6  Deep rinse cycle means a rinse cycle in which the clothes container is filled with water to a selected level and the clothes load is rinsed by agitating it or tumbling it through the water.

1.7  Energy test cycle for a basic model means (A) the cycle recommended by the manufacturer for washing cotton or linen clothes, and includes all wash/rinse temperature selections and water levels offered in that cycle, and (B) for each other wash/rinse temperature selection or water level available on that basic model, the portion(s) of other cycle(s) with that temperature selection or water level that, when tested pursuant to these test procedures, will contribute to an accurate representation of the energy consumption of the basic model as used by consumers. Any cycle under (A) or (B) shall include the agitation/tumble operation, spin speed(s), wash times, and rinse times applicable to that cycle, including water heating time for water heating clothes washers.

1.8  Load use factor means the percentage of the total number of wash loads that a user would wash a particular size (weight) load.

1.9  Manual control system means a clothes washer control system which requires that the consumer make the choices that determine washer operation or washing conditions, such as, for example, wash/rinse temperature selections, and wash time before starting the cycle.

1.10  Manual water fill control system means a clothes washer water fill control system which requires the consumer to determine or select the water fill level.

1.11  Modified energy factor means the quotient of the cubic foot (or liter) capacity of the clothes container divided by the total clothes washer energy consumption per cycle, with such energy consumption expressed as the sum of the machine electrical energy consumption, the hot water energy consumption, and the energy required for removal of the remaining moisture in the wash load.

1.12  Non-water-heating clothes washer means a clothes washer which does not have an internal water heating device to generate hot water.

1.13  Spray rinse cycle means a rinse cycle in which water is sprayed onto the clothes for a period of time without maintaining any specific water level in the clothes container.

1.14  Standard means a clothes washer which has a clothes container capacity of 1.6 ft³ (45 L) or greater.

1.15  Temperature use factor means, for a particular wash/rinse temperature setting, the percentage of the total number of wash loads that an average user would wash with that setting.

1.16  Thermostatically controlled water valves means clothes washer controls that have the ability to sense and adjust the hot and cold supply water.

1.17  Uniformly distributed warm wash temperature selection(s) means (A) multiple warm wash selections for which the warm wash water temperatures have a linear relationship with all discrete warm wash selections when the water temperatures are plotted against equally spaced consecutive warm wash selections between the hottest warm wash and the coldest warm wash. If the warm wash has infinite selections, the warm wash water temperature has a linear relationship with the distance on the selection device (e.g. dial angle or slide movement) between the hottest warm wash and the coldest warm wash. The criteria for a linear relationship as specified above is that the difference between the actual water temperature at any warm wash selection and the point where that temperature is depicted on the temperature/selection line formed by connecting the warmest and the coldest warm selections is less than ±5 percent. In all cases, the mean water temperature of the warmest and the coldest warm selections must coincide with the mean of the “hot wash” (maximum wash temperature ≤135 °F (57.2 °C)) and “cold wash” (minimum wash temperature) water temperatures within ±3.8 °F (±2.1 °C); or (B) on a clothes washer with only one warm wash temperature selection, a warm wash temperature selection with a water temperature that coincides with the mean of the “hot wash” (maximum wash temperature ≤135 °F (57.2 °C)) and “cold wash” (minimum wash temperature) water temperatures within ±3.8 °F (±2.1 °C).

1.18  Warm wash means all wash temperature selections that are below the hottest hot, less than 135 °F (57.2 °C), and above the coldest cold temperature selection.

1.19  Water consumption factor means the quotient of the total weighted per-cycle water consumption divided by the cubic foot (or liter) capacity of the clothes washer.

1.20  Water-heating clothes washer means a clothes washer where some or all of the hot water for clothes washing is generated by a water heating device internal to the clothes washer.

1.21  Symbol usage. The following identity relationships are provided to help clarify the symbology used throughout this procedure.

E—Electrical Energy Consumption

H—Hot Water Consumption

C—Cold Water Consumption

R—Hot Water Consumed by Warm Rinse

ER—Electrical Energy Consumed by Warm Rinse

TUF—Temperature Use Factor

HE—Hot Water Energy Consumption

F—Load Usage Factor

Q—Total Water Consumption

ME—Machine Electrical Energy Consumption

RMC—Remaining Moisture Content

WI—Initial Weight of Dry Test Load

WC—Weight of Test Load After Extraction

m—Extra Hot Wash (maximum wash temp. >135 °F (57.2 °C.))

h—Hot Wash (maximum wash temp. ≤135 °F (57.2 °C.))

w—Warm Wash

c—Cold Wash (minimum wash temp.)

r—Warm Rinse (hottest rinse temp.)

x or max—Maximum Test Load

a or avg—Average Test Load

n or min—Minimum Test Load

The following examples are provided to show how the above symbols can be used to define variables:

Em_x=“Electrical Energy Consumption” for an “Extra Hot Wash” and “Maximum Test Load”

R_a=“Hot Water Consumed by Warm Rinse” for the “Average Test Load”

TUF_m=“Temperature Use Factor” for an “Extra Hot Wash”

HE_min=“Hot Water Energy Consumption” for the “Minimum Test Load”

1.22  Cold rinse means the coldest rinse temperature available on the machine (and should be the same rinse temperature selection tested in 3.7 of this appendix).

1.23  Warm rinse means the hottest rinse temperature available on the machine (and should be the same rinse temperature selection tested in 3.7 of this appendix).

2. Testing Conditions

2.1  Installation. Install the clothes washer in accordance with manufacturer's instructions.

2.2  Electrical energy supply. Maintain the electrical supply at the clothes washer terminal block within 2 percent of 120, 120/240, or 120/208Y volts as applicable to the particular terminal block wiring system and within 2 percent of the nameplate frequency as specified by the manufacturer. If the clothes washer has a dual voltage conversion capability, conduct test at the highest voltage specified by the manufacturer.

2.3  Supply Water.

2.3.1  Clothes washers in which electrical energy consumption or water energy consumption are affected by the inlet water temperature. (For example, water heating clothes washers or clothes washers with thermostatically controlled water valves.). The temperature of the hot water supply at the water inlets shall not exceed 135 °F (57.2 °C) and the cold water supply at the water inlets shall not exceed 60 °F (15.6 °C). A water meter shall be installed in both the hot and cold water lines to measure water consumption.

2.3.2  Clothes washers in which electrical energy consumption and water energy consumption are not affected by the inlet water temperature. The temperature of the hot water supply shall be maintained at 135 °F±5 °F (57.2 °C±2.8 °C) and the cold water supply shall be maintained at 60 °F±5 °F (15.6 °C±2.8 °C). A water meter shall be installed in both the hot and cold water lines to measure water consumption.

2.4  Water pressure. The static water pressure at the hot and cold water inlet connection of the clothes washer shall be maintained at 35 pounds per square inch gauge (psig) ±2.5 psig (241.3 kPa±17.2 kPa) during the test. The static water pressure for a single water inlet connection shall be maintained at 35 psig±2.5 psig (241.3 kPa±17.2 kPa) during the test. A water pressure gauge shall be installed in both the hot and cold water lines to measure water pressure.

2.5  Instrumentation. Perform all test measurements using the following instruments, as appropriate:

2.5.1  Weighing scales.

2.5.1.1  Weighing scale for test cloth. The scale shall have a resolution of no larger than 0.2 oz (5.7 g) and a maximum error no greater than 0.3 percent of the measured value.

2.5.1.2  Weighing scale for clothes container capacity measurements. The scale should have a resolution no larger than 0.50 lbs (0.23 kg) and a maximum error no greater than 0.5 percent of the measured value.

2.5.2  Watt-hour meter. The watt-hour meter shall have a resolution no larger than 1 Wh (3.6 kJ) and a maximum error no greater than 2 percent of the measured value for any demand greater than 50 Wh (180.0 kJ).

2.5.3  Temperature measuring device. The device shall have an error no greater than ±1 °F (±0.6 °C) over the range being measured.

2.5.4  Water meter. The water meter shall have a resolution no larger than 0.1 gallons (0.4 liters) and a maximum error no greater than 2 percent for the water flow rates being measured.

2.5.5  Water pressure gauge. The water pressure gauge shall have a resolution of 1 pound per square inch gauge (psig) (6.9 kPa) and shall have an error no greater than 5 percent of any measured value.

2.6  Test cloths.

2.6.1  Energy Test Cloth. The energy test cloth shall be made from energy test cloth material, as specified in 2.6.4, that is 24 inches by 36 inches (61.0 cm by 91.4 cm) and has been hemmed to 22 inches by 34 inches (55.9 cm by 86.4 cm) before washing. The energy test cloth shall be clean and shall not be used for more than 60 test runs (after preconditioning as specified in 2.6.3 of this appendix). All energy test cloth must be permanently marked identifying the lot number of the material. Mixed lots of material shall not be used for testing the clothes washers.

2.6.1.1  The energy test cloth shall not be used for more than 25 test runs and shall be clean and consist of the following:

(A) Pure finished bleached cloth, made with a momie or granite weave, which is 50 percent cotton and 50 percent polyester and weighs 5.75 ounces per square yard (195.0 g/m² ) and has 65 ends on the warp and 57 picks on the fill; and

(B) Cloth material that is 24 inches by 36 inches (61.0 cm by 91.4 cm) and has been hemmed to 22 inches by 34 inches (55.9 cm by 86.4 cm) before washing. The maximum shrinkage after five washes shall not be more than four percent on the length and width.

2.6.1.2  The new test cloths, including energy test cloths and energy stuffer cloths, shall be pre-conditioned in a clothes washer in the following manner:

2.6.1.2.1  Wash the test cloth using a commercially available clothes washing detergent that is suitable for 135 °F (57.2 °C) wash water as recommended by the manufacturer, with the washer set on maximum water level. Place detergent in washer and then place the new load to be conditioned in the washer. Wash the load for ten minutes in soft water (17ppm or less). Wash water is to be hot, and controlled at 135 °F±5 °F (57.2 °C ±2.8 °C). Rinse water temperature is to be cold, and controlled at 60 °F ±5 °F (15.6 °C ±2.8 °C). Rinse the load through a second rinse using the same water temperature (if an optional second rinse is available on the clothes washer, use it).

2.6.1.2.2  Dry the load.

2.6.1.2.3  A final cycle is to be hot water wash with no detergent followed by two cold water rinses.

2.6.1.2.4  Dry the load.

2.6.2  Energy Stuffer Cloth. The energy stuffer cloth shall be made from energy test cloth material, as specified in 2.6.4, and shall consist of pieces of material that are 12 inches by 12 inches (30.5 cm by 30.5 cm) and have been hemmed to 10 inches by 10 inches (25.4 cm by 25.4 cm) before washing. The energy stuffer cloth shall be clean and shall not be used for more than 60 test runs (after preconditioning as specified in 2.6.3 of this appendix). All energy stuffer cloth must be permanently marked identifying the lot number of the material. Mixed lots of material shall not be used for testing the clothes washers.

2.6.3  Preconditioning of Test Cloths. The new test cloths, including energy test cloths and energy stuffer cloths, shall be pre-conditioned in a clothes washer in the following manner:

2.6.3.1  Perform 5 complete normal wash-rinse-spin cycles, the first two with AHAM Standard detergent 2A and the last three without detergent. Place the test cloth in a clothes washer set at the maximum water level. Wash the load for ten minutes in soft water (17 ppm hardness or less) using 6.0 grams per gallon of water of AHAM Standard detergent 2A. The wash temperature is to be controlled to 135 °F ±5 °F (57.2 °C ±2.8 °C) and the rinse temperature is to be controlled to 60 °F ±5 °F (15.6 °C ±2.8 °C). Repeat the cycle with detergent and then repeat the cycle three additional times without detergent, bone drying the load between cycles (total of five wash and rinse cycles).

2.6.4  Energy test cloth material. The energy test cloths and energy stuffer cloths shall be made from fabric meeting the following specifications. The material should come from a roll of material with a width of approximately 63 inches and approximately 500 yards per roll, however, other sizes maybe used if they fall within the specifications.

2.6.4.1  Nominal fabric type. Pure finished bleached cloth, made with a momie or granite weave, which is nominally 50 percent cotton and 50 percent polyester.

2.6.4.2  The fabric weight shall be 5.60 ounces per square yard (190.0 g/m² ), ±5 percent.

2.6.4.3  The thread count shall be 61 × 54 per inch (warp × fill), ±2 percent.

2.6.4.4  The warp yarn and filling yarn shall each have fiber content of 50 percent ±4 percent cotton, with the balance being polyester, and be open end spun, 15/1 ±5 percent cotton count blended yarn.

2.6.4.5  Water repellent finishes, such as fluoropolymer stain resistant finishes shall not be applied to the test cloth. The absence of such finishes shall be verified by:

2.6.4.5.1  American Association of Textile Chemists and Colorists (AATCC) Test Method 118—1997, Oil Repellency: Hydrocarbon Resistance Test (reaffirmed 1997), of each new lot of test cloth (when purchased from the mill) to confirm the absence of Scotchguard^TM or other water repellent finish (required scores of “D” across the board).

2.6.4.5.2  American Association of Textile Chemists and Colorists (AATCC) Test Method 79–2000, Absorbency of Bleached Textiles (reaffirmed 2000), of each new lot of test cloth (when purchased from the mill) to confirm the absence of Scotchguard^TM or other water repellent finish (time to absorb one drop should be on the order of 1 second).

2.6.4.5.3  The standards listed in 2.6.4.5.1 and 2.6.4.5.2 of this appendix which are not otherwise set forth in this part 430 are incorporated by reference. The material listed in this paragraph has been approved for incorporation by reference by the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR Part 51. Any subsequent amendment to a standard by the standard-setting organization will not affect the DOE test procedures unless and until amended by DOE. Material is incorporated as it exists on the date of the approval and notice of any change in the material will be published in the Federal Register. The standards incorporated by reference are the American Association of Textile Chemists and Colorists Test Method 118–1997, Oil Repellency: Hydrocarbon Resistance Test (reaffirmed 1997) and Test Method 79–2000, Absorbency of Bleached Textiles (reaffirmed 2000).

(a) The above standards incorporated by reference are available for inspection at:

(i) National Archives and Records Administration (NARA). For information on the availability of this material at NARA, call 202–741–6030, or go to: http://www.archives.gov/federal_register/code_of_federal_regulations/ibr_locations.php.

(ii) U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Hearings and Dockets, “Energy Conservation Program for Consumer Products: Clothes Washer Energy Conservation Standards,” Docket No. EE—RM–94–403, Forrestal Building, 1000 Independence Avenue, SW, Washington, DC.

(b) Copies of the above standards incorporated by reference can be obtained from the American Association of Textile Chemists and Colorists, P.O. Box 1215, Research Triangle Park, NC 27709, telephone (919) 549–8141, telefax (919) 549–8933, or electronic mail: [email protected].

2.6.4.6  The moisture absorption and retention shall be evaluated for each new lot of test cloth by the Standard Extractor Remaining Moisture Content (RMC) Test specified in 2.6.5 of this appendix.

2.6.4.6.1  Repeat the Standard Extractor RMC Test in 2.6.5 of this appendix three times.

2.6.4.6.2  An RMC correction curve shall be calculated as specified in 2.6.6 of this appendix.

2.6.5  Standard Extractor RMC Test Procedure. The following procedure is used to evaluate the moisture absorption and retention characteristics of a lot of test cloth by measuring the RMC in a standard extractor at a specified set of conditions. Table 2.6.5 of this appendix is the matrix of test conditions. The 500g requirement will only be used if a clothes washer design can achieve spin speeds in the 500g range. When this matrix is repeated 3 times, a total of 48 extractor RMC test runs are required. For the purpose of the extractor RMC test, the test cloths may be used for up to 60 test runs (after preconditioning as specified in 2.6.3 of this appendix).

2.6.5.1  The standard extractor RMC tests shall be run in a Bock Model 215 extractor (having a basket diameter of 19.5 inches, length of 12 inches, and volume of 2.1 ft³ ), with a variable speed drive (Bock Engineered Products, P.O. Box 5127, Toledo, OH 43611) or an equivalent extractor with same basket design (i.e. diameter, length, volume, and hole configuration) and variable speed drive.

2.6.5.2 Test Load. Test cloths shall be preconditioned in accordance with 2.6.3 of this appendix. The load size shall be 8.4 lbs., consistent with 3.8.1 of this appendix.

2.6.5.3  Procedure.

2.6.5.3.1  Record the “bone-dry” weight of the test load (WI).

2.6.5.3.2  Soak the test load for 20 minutes in 10 gallons of soft (<17 ppm) water. The entire test load shall be submerged. The water temperature shall be 100 °F ±5 °F.

2.6.5.3.3  Remove the test load and allow water to gravity drain off of the test cloths. Then manually place the test cloths in the basket of the extractor, distributing them evenly by eye. Spin the load at a fixed speed corresponding to the intended centripetal acceleration level (measured in units of the acceleration of gravity, g) ±1 g for the intended time period ±5 seconds.

2.6.5.3.4  Record the weight of the test load immediately after the completion of the extractor spin cycle (WC).

2.6.5.3.5  Calculate the RMC as (WC-WI)/WI.

2.6.5.3.6  The RMC of the test load shall be measured at three (3) g levels: 100g; 200g; and 350g, using two different spin times at each g level: 4 minutes; and 15 minutes. If a clothes washer design can achieve spin speeds in the 500g range then the RMC of the test load shall be measured at four (4) g levels: 100g; 200g; 350g; and 500g, using two different spin times at each g level: 4 minutes; and 15 minutes.

2.6.5.4  Repeat 2.6.5.3 of this appendix using soft (<17 ppm) water at 60 °F ±5 °F.

2.6.6  Calculation of RMC correction curve.

2.6.6.1  Average the values of 3 test runs and fill in table 2.6.5 of this appendix. Perform a linear least-squares fit to relate the standard RMC (RMC_standard) values (shown in table 2.6.6.1 of this appendix) to the values measured in 2.6.5 of this appendix:

(RMC_cloth): RMC_standard ∼ A * RMC_cloth + B

Where A and B are coefficients of the linear least-squares fit.

2.6.6.2.  Perform an analysis of variance test using two factors, spin speed and lot, to check the interaction of speed and lot. Use the values from Table 2.6.5 and Table 2.6.6.1 in the calculation. The “P” value in the variance analysis shall be greater than or equal to 0.1. If the “P” value is less than 0.1 the test cloth is unacceptable. “P” is a theoretically based probability of interaction based on an analysis of variance.

2.6.7  Application of RMC correction curve.

2.6.7.1  Using the coefficients A and B calculated in 2.6.6.1 of this appendix:

RMC_corr = A * RMC + B

2.6.7.2  Substitute RMC_corr values in calculations in 3.8 of this appendix.

2.7  Test Load Sizes. Maximum, minimum, and, when required, average test load sizes shall be determined using Table 5.1 and the clothes container capacity as measured in 3.1.1 through 3.1.5. Test loads shall consist of energy test cloths, except that adjustments to the test loads to achieve proper weight can be made by the use of energy stuffer cloths with no more than 5 stuffer clothes per load.

2.8  Use of Test Loads. Table 2.8 defines the test load sizes and corresponding water fill settings which are to be used when measuring water and energy consumptions. Adaptive water fill control system and manual water fill control system are defined in section 1 of this appendix:

2.8.1  The test load sizes to be used to measure RMC are specified in section 3.8.1.

2.8.2  Test loads for energy and water consumption measurements shall be bone dry prior to the first cycle of the test, and dried to a maximum of 104 percent of bone dry weight for subsequent testing.

2.8.3  Load the energy test cloths by grasping them in the center, shaking them to hang loosely and then put them into the clothes container prior to activating the clothes washer.

2.9  Pre-conditioning.

2.9.1  Nonwater-heating clothes washer. If the clothes washer has not been filled with water in the preceding 96 hours, pre-condition it by running it through a cold rinse cycle and then draining it to ensure that the hose, pump, and sump are filled with water.

2.9.2  Water-heating clothes washer. If the clothes washer has not been filled with water in the preceding 96 hours, or if it has not been in the test room at the specified ambient conditions for 8 hours, pre-condition it by running it through a cold rinse cycle and then draining it to ensure that the hose, pump, and sump are filled with water.

2.10  Wash time setting. If one wash time is prescribed in the energy test cycle, that shall be the wash time setting; otherwise, the wash time setting shall be the higher of either the minimum, or 70 percent of the maximum wash time available in the energy test cycle.

2.11  Test room temperature for water-heating clothes washers. Maintain the test room ambient air temperature at 75 °F±5 °F (23.9 °C±2.8 °C).

3. Test Measurements

3.1  Clothes container capacity. Measure the entire volume which a dry clothes load could occupy within the clothes container during washer operation according to the following procedures:

3.1.1  Place the clothes washer in such a position that the uppermost edge of the clothes container opening is leveled horizontally, so that the container will hold the maximum amount of water.

3.1.2  Line the inside of the clothes container with 2 mil (0.051 mm) plastic sheet. All clothes washer components which occupy space within the clothes container and which are recommended for use with the energy test cycle shall be in place and shall be lined with 2 mil (0.051 mm) plastic sheet to prevent water from entering any void space.

3.1.3  Record the total weight of the machine before adding water.

3.1.4  Fill the clothes container manually with either 60 °F±5 °F (15.6 °C±2.8 °C) or 100 °F±10 °F (37.8 °C±5.5 °C) water to its uppermost edge. Measure and record the weight of water, W, in pounds.

3.1.5  The clothes container capacity is calculated as follows:

C=W/d.

where:

C=Capacity in cubic feet (liters).

W=Mass of water in pounds (kilograms).

d=Density of water (62.0 lbs/ft³ for 100 °F (993 kg/m³ for 37.8 °C) or 62.3 lbs/ft³ for 60 °F (998 kg/m³ for 15.6 °C)).

3.2  Procedure for measuring water and energy consumption values on all automatic and semi-automatic washers. All energy consumption tests shall be performed under the energy test cycle(s), unless otherwise specified. Table 3.2 defines the sections below which govern tests of particular clothes washers, based on the number of wash/rinse temperature selections available on the model, and also, in some instances, method of water heating. The procedures prescribed are applicable regardless of a clothes washer's washing capacity, loading port location, primary axis of rotation of the clothes container, and type of control system.

3.2.1  Inlet water temperature and the wash/rinse temperature settings.

3.2.1.1  For automatic clothes washers set the wash/rinse temperature selection control to obtain the wash water temperature desired (extra hot, hot, warm, or cold) and cold rinse, and open both the hot and cold water faucets.

3.2.1.2  For semi-automatic washers: (1) For hot water temperature, open the hot water faucet completely and close the cold water faucet; (2) for warm inlet water temperature, open both hot and cold water faucets completely; (3) for cold water temperature, close the hot water faucet and open the cold water faucet completely.

3.2.1.3  Determination of warm wash water temperature(s) to decide whether a clothes washer has uniformly distributed warm wash temperature selections. The wash water temperature, Tw, of each warm water wash selection shall be calculated or measured.

For non-water-heating clothes washers, calculate Tw as follows:

Tw( °F)=((Hw×135 °F)+(Cw×60 °F))/(Hw+Cw)

    or

Tw( °C)=((Hw×57.2 °C)+(Cw×15.6 °C))/(Hw+Cw)

where:

Hw=Hot water consumption of a warm wash

Cw=Cold water consumption of a warm wash

For water-heating clothes washers, measure and record the temperature of each warm wash selection after fill.

3.2.2  Total water consumption during the energy test cycle shall be measured, including hot and cold water consumption during wash, deep rinse, and spray rinse.

3.2.3  Clothes washers with adaptive water fill/manual water fill control systems

3.2.3.1  Clothes washers with adaptive water fill control system and alternate manual water fill control systems. If a clothes washer with an adaptive water fill control system allows consumer selection of manual controls as an alternative, then both manual and adaptive modes shall be tested and, for each mode, the energy consumption (HE_T, ME_T, and D_E) and water consumption (Q_T), values shall be calculated as set forth in section 4. Then the average of the two values (one from each mode, adaptive and manual) for each variable shall be used in section 4 for the clothes washer.

3.2.3.2  Clothes washers with adaptive water fill control system.

3.2.3.2.1.  Not user adjustable. The maximum, minimum, and average water levels as defined in the following sections shall be interpreted to mean that amount of water fill which is selected by the control system when the respective test loads are used, as defined in Table 2.8. The load usage factors which shall be used when calculating energy consumption values are defined in Table 4.1.3.

3.2.3.2.2  User adjustable. Four tests shall be conducted on clothes washers with user adjustable adaptive water fill controls which affect the relative wash water levels. The first test shall be conducted with the maximum test load and with the adaptive water fill control system set in the setting that will give the most energy intensive result. The second test shall be conducted with the minimum test load and with the adaptive water fill control system set in the setting that will give the least energy intensive result. The third test shall be conducted with the average test load and with the adaptive water fill control system set in the setting that will give the most energy intensive result for the given test load. The fourth test shall be conducted with the average test load and with the adaptive water fill control system set in the setting that will give the least energy intensive result for the given test load. The energy and water consumption for the average test load and water level, shall be the average of the third and fourth tests.

3.2.3.3  Clothes washers with manual water fill control system. In accordance with Table 2.8, the water fill selector shall be set to the maximum water level available on the clothes washer for the maximum test load size and set to the minimum water level for the minimum test load size. The load usage factors which shall be used when calculating energy consumption values are defined in Table 4.1.3.

3.3  “Extra Hot Wash” (Max Wash Temp >135 °F (57.2 °C)) for water heating clothes washers only. Water and electrical energy consumption shall be measured for each water fill level and/or test load size as specified in 3.3.1 through 3.3.3 for the hottest wash setting available.

3.3.1  Maximum test load and water fill. Hot water consumption (Hm_x), cold water consumption (Cm_x), and electrical energy consumption (Em_x) shall be measured for an extra hot wash/cold rinse energy test cycle, with the controls set for the maximum water fill level. The maximum test load size is to be used and shall be determined per Table 5.1.

3.3.2  Minimum test load and water fill. Hot water consumption (Hm_n), cold water consumption (Cm_n), and electrical energy consumption (Em_n) shall be measured for an extra hot wash/cold rinse energy test cycle, with the controls set for the minimum water fill level. The minimum test load size is to be used and shall be determined per Table 5.1.

3.3.3  Average test load and water fill. For clothes washers with an adaptive water fill control system, measure the values for hot water consumption (Hm_a), cold water consumption (Cm_a), and electrical energy consumption (Em_a) for an extra hot wash/cold rinse energy test cycle, with an average test load size as determined per Table 5.1.

3.4  “Hot Wash” (Max Wash Temp≤135 °F (57.2 °C)). Water and electrical energy consumption shall be measured for each water fill level or test load size as specified in 3.4.1 through 3.4.3 for a 135 °F (57.2 °C)) wash, if available, or for the hottest selection less than 135 °F (57.2 °C)).

3.4.1  Maximum test load and water fill. Hot water consumption (Hh_x), cold water consumption (Ch_x), and electrical energy consumption (Eh_x) shall be measured for a hot wash/cold rinse energy test cycle, with the controls set for the maximum water fill level. The maximum test load size is to be used and shall be determined per Table 5.1.

3.4.2  Minimum test load and water fill. Hot water consumption (Hh_n), cold water consumption (Ch_n), and electrical energy consumption (Eh_n) shall be measured for a hot wash/cold rinse energy test cycle, with the controls set for the minimum water fill level. The minimum test load size is to be used and shall be determined per Table 5.1.

3.4.3  Average test load and water fill. For clothes washers with an adaptive water fill control system, measure the values for hot water consumption (Hh_a), cold water consumption (Ch_a), and electrical energy consumption (Eh_a) for a hot wash/cold rinse energy test cycle, with an average test load size as determined per Table 5.1.

3.5  “Warm Wash.” Water and electrical energy consumption shall be determined for each water fill level and/or test load size as specified in 3.5.1 through 3.5.2.3 for the applicable warm water wash temperature(s).

3.5.1  Clothes washers with uniformly distributed warm wash temperature selection(s). The reportable values to be used for the warm water wash setting shall be the arithmetic average of the measurements for the hot and cold wash selections. This is a calculation only, no testing is required.

3.5.2  Clothes washers that lack uniformly distributed warm wash temperature selections. For a clothes washer with fewer than four discrete warm wash selections, test all warm wash temperature selections. For a clothes washer that offers four or more warm wash selections, test at all discrete selections, or test at 25 percent, 50 percent, and 75 percent positions of the temperature selection device between the hottest hot (≤135 °F (57.2 °C)) wash and the coldest cold wash. If a selection is not available at the 25, 50 or 75 percent position, in place of each such unavailable selection use the next warmer setting. Each reportable value to be used for the warm water wash setting shall be the arithmetic average of all tests conducted pursuant to this section.

3.5.2.1  Maximum test load and water fill. Hot water consumption (Hw_x), cold water consumption (Cw_x), and electrical energy consumption (Ew_x) shall be measured with the controls set for the maximum water fill level. The maximum test load size is to be used and shall be determined per Table 5.1.

3.5.2.2  Minimum test load and water fill. Hot water consumption (Hw_n), cold water consumption (Cw_n), and electrical energy consumption (Ew_n) shall be measured with the controls set for the minimum water fill level. The minimum test load size is to be used and shall be determined per Table 5.1.

3.5.2.3  Average test load and water fill. For clothes washers with an adaptive water fill control system, measure the values for hot water consumption (Hw_a), cold water consumption (Cw_a), and electrical energy consumption (Ew_a) with an average test load size as determined per Table 5.1.

3.6  “Cold Wash” (Minimum Wash Temperature Selection). Water and electrical energy consumption shall be measured for each water fill level or test load size as specified in 3.6.1 through 3.6.3 for the coldest wash temperature selection available.

3.6.1  Maximum test load and water fill. Hot water consumption (Hc_x), cold water consumption (Cc_x), and electrical energy consumption (Ec_x) shall be measured for a cold wash/cold rinse energy test cycle, with the controls set for the maximum water fill level. The maximum test load size is to be used and shall be determined per Table 5.1.

3.6.2  Minimum test load and water fill. Hot water consumption (Hc_n), cold water consumption (Cc_n), and electrical energy consumption (Ec_n) shall be measured for a cold wash/cold rinse energy test cycle, with the controls set for the minimum water fill level. The minimum test load size is to be used and shall be determined per Table 5.1.

3.6.3  Average test load and water fill. For clothes washers with an adaptive water fill control system, measure the values for hot water consumption (Hc_a), cold water consumption (Cc_a), and electrical energy consumption (Ec_a) for a cold wash/cold rinse energy test cycle, with an average test load size as determined per Table 5.1.

3.7  Warm Rinse. Tests in sections 3.7.1 and 3.7.2 shall be conducted with the hottest rinse temperature available. If multiple wash temperatures are available with the hottest rinse temperature, any “warm wash” temperature may be selected to conduct the tests.

3.7.1  For the rinse only, measure the amount of hot water consumed by the clothes washer including all deep and spray rinses, for the maximum (R_x), minimum (R_n), and, if required by section 3.5.2.3, average (R_a) test load sizes or water fill levels.

3.7.2  Measure the amount of electrical energy consumed by the clothes washer to heat the rinse water only, including all deep and spray rinses, for the maximum (ER_x), minimum (ER_n), and, if required by section 3.5.2.3, average (ER_a), test load sizes or water fill levels.

3.8  Remaining Moisture Content:

3.8.1  The wash temperature will be the same as the rinse temperature for all testing. Use the maximum test load as defined in Table 5.1 and section 3.1 for testing.

3.8.2  For clothes washers with cold rinse only:

3.8.2.1  Record the actual ‘bone dry’ weight of the test load (WI_max), then place the test load in the clothes washer.

3.8.2.2  Set water level selector to maximum fill.

3.8.2.3  Run the energy test cycle.

3.8.2.4  Record the weight of the test load immediately after completion of the energy test cycle (WC_max).

3.8.2.5  Calculate the remaining moisture content of the maximum test load, RMC_MAX, expressed as a percentage and defined as:

RMC_max=((WC_max−WI_max)/WI_max)×100%

3.8.3  For clothes washers with cold and warm rinse options:

3.8.3.1  Complete steps 3.8.2.1 through 3.8.2.4 for cold rinse. Calculate the remaining moisture content of the maximum test load for cold rinse, RMC_COLD, expressed as a percentage and defined as:

RMC_COLD=((WC_max−WI_max)/WI_max)×100%

3.8.3.2  Complete steps 3.8.2.1 through 3.8.2.4 for warm rinse. Calculate the remaining moisture content of the maximum test load for warm rinse, RMC_WARM, expressed as a percentage and defined as:

RMC_WARM=((WC_max−WI_max)/WI_max)×100%

3.8.3.3  Calculate the remaining moisture content of the maximum test load, RMC_max, expressed as a percentage and defined as:

RMC_max=RMC_COLD×(1-TUF_r)+RMC_WARM×(TUF_r).

where:

TUF_r is the temperature use factor for warm rinse as defined in Table 4.1.1.

3.8.4  Clothes washers which have options that result in different RMC values, such as multiple selection of spin speeds or spin times, that are available in the energy test cycle, shall be tested at the maximum and minimum extremes of the available options, excluding any “no spin” (zero spin speed) settings, in accordance with requirements in 3.8.2 or 3.8.3. The calculated RMC_{max extraction} and RMC_{min extraction} at the maximum and minimum settings, respectively, shall be combined as follows and the final RMC to be used in section 4.3 shall be:

RMC = 0.75×RMC_{max extraction}+0.25×

    RMC_{min extraction}

4. Calculation of Derived Results From Test Measurements

4.1  Hot water and machine electrical energy consumption of clothes washers.

4.1.1  Per-cycle temperature-weighted hot water consumption for maximum, average, and minimum water fill levels using each appropriate load size as defined in section 2.8 and Table 5.1. Calculate for the cycle under test the per-cycle temperature weighted hot water consumption for the maximum water fill level, Vh_x, the average water fill level, Vh_a, and the minimum water fill level, Vh_n, expressed in gallons per cycle (or liters per cycle) and defined as:

(a) Vh_x=[Hm_x×TUF_m]+[Hh_x×TUF_h]+[Hw_x ×TUF_w]+[Hc_x×TUF_c]+[R_x×TUF_r]

(b) Vh_a=[Hm_a×TUF_m]+[Hh_a×TUF_h]+[Hw_a ×TUF_w]+[Hc_a×TUF_c]+[R_a×TUF_r]

(c) Vh_n=[Hm_n×TUF_m]+[Hh_n×TUF_h]+[Hw_n ×TUF_w]+[Hc_n×TUF_c]+[R_n×TUF_r]

where:

Hm_x, Hm_a, and Hm_n, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill, respectively, for the extra-hot wash cycle with the appropriate test loads as defined in section 2.8.

Hh_x, Hh_a, and Hh_n, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill, respectively, for the hot wash cycle with the appropriate test loads as defined in section 2.8.

Hw_x, Hw_a, and Hw_n, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill, respectively, for the warm wash cycle with the appropriate test loads as defined in section 2.8.

Hc_x, Hc_a, and Hc_n, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill, respectively, for the cold wash cycle with the appropriate test loads as defined in section 2.8.

R_x, R_a, and R_n are the reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill, respectively, for the warm rinse cycle and the appropriate test loads as defined in section 2.8.

TUF_m, TUF_h, TUF_w, TUF_c, and TUF_r are temperature use factors for extra hot wash, hot wash, warm wash, cold wash, and warm rinse temperature selections, respectively, and are as defined in Table 4.1.1.

4.1.2  Total per-cycle hot water energy consumption for all maximum, average, and minimum water fill levels tested. Calculate the total per-cycle hot water energy consumption for the maximum water fill level, HE_max, the minimum water fill level, HE_min, and the average water fill level, HE_avg, expressed in kilowatt-hours per cycle and defined as:

(a) HE_max = [Vh_x×T×K]=Total energy when a maximum load is tested.

(b) HE_avg = [Vh_a×T×K]=Total energy when an average load is tested.

(c) HE_min = [Vh_n×T×K]=Total energy when a minimum load is tested.

where:

T=Temperature rise=75 °F (41.7 °C).

K=Water specific heat in kilowatt-hours per gallon degree F=0.00240 (0.00114 kWh/L-°C).

Vh_x Vh_a, and Vh_n, are as defined in 4.1.1.

4.1.3  Total weighted per-cycle hot water energy consumption. Calculate the total weighted per cycle hot water energy consumption, HE_T, expressed in kilowatt-hours per cycle and defined as:

HE_T=[HE_max×F_max]+[HE_avg×F_avg]+[HE_mn×F_min]

where:

HE_max, HE_avg, and HE_min are as defined in 4.1.2.

F_max, F_avg, and F_min are the load usage factors for the maximum, average, and minimum test loads based on the size and type of control system on the washer being tested. The values are as shown in table 4.1.3.

4.1.4  Total per-cycle hot water energy consumption using gas-heated or oil-heated water. Calculate for the energy test cycle the per-cycle hot water consumption, HE_TG, using gas heated or oil-heated water, expressed in Btu per cycle (or megajoules per cycle) and defined as:

HE_TG=H_T×1/e×3412 Btu/kWh or HE_TG=HE_T×1/e×3.6 MJ/kWh

where:

e=Nominal gas or oil water heater efficiency=0.75.

HE_T=As defined in 4.1.3.

4.1.5  Per-cycle machine electrical energy consumption for all maximum, average, and minimum test load sizes. Calculate the total per-cycle machine electrical energy consumption for the maximum water fill level, ME_max, the minimum water fill level, ME_min, and the average water fill level, ME_avg, expressed in kilowatt-hours per cycle and defined as:

(a)ME_max= [Em_x×TUF_m]+ [Eh_x×TUF_h]+ [Ew_x×TUF_w]+ [Ec_x×TUF_c]+ [ER_x×TUF_r]

(b) ME_avg= [Em_a×TUF_m]+ [Eh_a×TUF_h]+ [Ew_a×TUF_w]+ [Ec_a×TUF_c]+ [ER_a×TUF_r]

(c) ME_min= [Em_n×TUF_m]+ [Eh_n×TUF_h]+ [Ew_n×TUF_w]+ [Ec_n×xTUF_c]+ [ER_n×TUF_r]

where:

Em_x, Em_a, and Em_n, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the extra-hot wash cycle.

Eh_x, Eh_a, and Eh_n, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the hot wash cycle.

Ew_x, Ew_a, and Ew_n, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the warm wash cycle.

Ec_x, Ec_a, and Ec_n, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the cold wash cycle.

ER_x, ER_a, ER_n, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the warm rinse cycle per definitions in 3.7.2 of this appendix.

TUF_m, TUF_h, TUF_w, TUF_c, and TUF_r are as defined in Table 4.1.1.

4.1.6  Total weighted per-cycle machine electrical energy consumption. Calculate the total per cycle load size weighted energy consumption, ME_T, expressed in kilowatt-hours per cycle and defined as:

ME_T=[ME_max× F_max]+[ME_avg× F_avg]+[ME_min× F_min]

where:

ME_max, ME_avg, and ME_min are as defined in 4.1.5.

F_max, F_avg, and F_min are as defined in Table 4.1.3.

4.1.7  Total per-cycle energy consumption when electrically heated water is used. Calculate for the energy test cycle the total per-cycle energy consumption, E_TE, using electrical heated water, expressed in kilowatt-hours per cycle and defined as:

E_TE=HE_T+ME_T

where:

ME_T=As defined in 4.1.6.

HE_T=As defined in 4.1.3.

4.2  Water consumption of clothes washers. (The calculations in this Section need not be performed to determine compliance with the energy conservation standards for clothes washers.)

4.2.1  Per-cycle water consumption. Calculate the maximum, average, and minimum total water consumption, expressed in gallons per cycle (or liters per cycle), for the cold wash/cold rinse cycle and defined as:

Q_max=[Hc_x+Cc_x]

Q_avg=[Hc_a+Cc_a]

Q_min=[Hc_n+Cc_n]

where:

Hc_x, Cc_x, Hc_a, Cc_a, Hc_n, and Cc_n are as defined in 3.6.

4.2.2  Total weighted per-cycle water consumption. Calculate the total weighted per cycle consumption, Q_T, expressed in gallons per cycle (or liters per cycle) and defined as:

Q_T=[Q_max×F_max]+[Q_avg×F_avg]+[Q_min×F_min]

where:

Q_max, Q_avg, and Q_min are as defined in 4.2.1.

F_max, F_avg, and F_min are as defined in table 4.1.3.

4.2.3  Water consumption factor. Calculate the water consumption factor, WCF, expressed in gallon per cycle per cubic feet (or liter per cycle per liter), as:

WCF=Q_T / C

where:

Q_T=as defined in section 4.2.2.

C = as defined in section 3.1.5.

4.3  Per-cycle energy consumption for removal of moisture from test load. Calculate the per-cycle energy required to remove the moisture of the test load, D_E, expressed in kilowatt-hours per cycle and defined as

D_E=(LAF)×(Maximum test load weight)×(RMC—4%)×(DEF)×(DUF)

where:

LAF=Load adjustment factor=0.52.

Test load weight=As required in 3.8.1, expressed in lbs/cycle.

RMC=As defined in 3.8.2.5, 3.8.3.3 or 3.8.4.

DEF=nominal energy required for a clothes dryer to remove moisture from clothes=0.5 kWh/lb (1.1 kWh/kg).

DUF=dryer usage factor, percentage of washer loads dried in a clothes dryer=0.84.

4.4  Modified energy factor. Calculate the modified energy factor, MEF, expressed in cubic feet per kilowatt-hour per cycle (or liters per kilowatt-hour per cycle) and defined as:

MEF=C/(E_TE + D_E)

where:

C=As defined in 3.1.5.

E_TE=As defined in 4.1.7.

D_E=As defined in 4.3.

4.5  Energy factor. Calculate the energy factor, EF, expressed in cubic feet per kilowatt-hour per cycle (or liters per kilowatt-hour per cycle) and defined as:

EF=C/E_TE

where:

C=As defined in 3.1.5.

E_TE=As defined in 4.1.7.

5. Test Loads

6. Waivers and Field Testing

6.1  Waivers and Field Testing for Non-conventional Clothes Washers. Manufacturers of nonconventional clothes washers, such as clothes washers with adaptive control systems, must submit a petition for waiver pursuant to 10 CFR 430.27 to establish an acceptable test procedure for that clothes washer. For these and other clothes washers that have controls or systems such that the DOE test procedures yield results that are so unrepresentative of the clothes washer's true energy consumption characteristics as to provide materially inaccurate comparative data, field testing may be appropriate for establishing an acceptable test procedure. The following are guidelines for field testing which may be used by manufacturers in support of petitions for waiver. These guidelines are not mandatory and the Department may determine that they do not apply to a particular model. Depending upon a manufacturer's approach for conducting field testing, additional data may be required. Manufacturers are encouraged to communicate with the Department prior to the commencement of field tests which may be used to support a petition for waiver. Section 6.3 provides an example of field testing for a clothes washer with an adaptive water fill control system. Other features, such as the use of various spin speed selections, could be the subject of field tests.

6.2  Nonconventional Wash System Energy Consumption Test. The field test may consist of a minimum of 10 of the nonconventional clothes washers (“test clothes washers”) and 10 clothes washers already being distributed in commerce (“base clothes washers”). The tests should include a minimum of 50 energy test cycles per clothes washer. The test clothes washers and base clothes washers should be identical in construction except for the controls or systems being tested. Equal numbers of both the test clothes washer and the base clothes washer should be tested simultaneously in comparable settings to minimize seasonal or consumer laundering conditions or variations. The clothes washers should be monitored in such a way as to accurately record the total energy consumption per cycle. At a minimum, the following should be measured and recorded throughout the test period for each clothes washer: Hot water usage in gallons (or liters), electrical energy usage in kilowatt-hours, and the cycles of usage.

The field test results would be used to determine the best method to correlate the rating of the test clothes washer to the rating of the base clothes washer. If the base clothes washer is rated at A kWh per year, but field tests at B kWh per year, and the test clothes washer field tests at D kWh per year, the test unit would be rated as follows:

A×(D/B)=G kWh per year

6.3  Adaptive water fill control system field test. Section 3.2.3.1 defines the test method for measuring energy consumption for clothes washers which incorporate control systems having both adaptive and alternate cycle selections. Energy consumption calculated by the method defined in section 3.2.3.1 assumes the adaptive cycle will be used 50 percent of the time. This section can be used to develop field test data in support of a petition for waiver when it is believed that the adaptive cycle will be used more than 50 percent of the time. The field test sample size should be a minimum of 10 test clothes washers. The test clothes washers should be totally representative of the design, construction, and control system that will be placed in commerce. The duration of field testing in the user's house should be a minimum of 50 energy test cycles, for each unit. No special instructions as to cycle selection or product usage should be given to the field test participants, other than inclusion of the product literature pack which would be shipped with all units, and instructions regarding filling out data collection forms, use of data collection equipment, or basic procedural methods. Prior to the test clothes washers being installed in the field test locations, baseline data should be developed for all field test units by conducting laboratory tests as defined by section 1 through section 5 of these test procedures to determine the energy consumption, water consumption, and remaining moisture content values. The following data should be measured and recorded for each wash load during the test period: wash cycle selected, the mode of the clothes washer (adaptive or manual), clothes load dry weight (measured after the clothes washer and clothes dryer cycles are completed) in pounds, and type of articles in the clothes load (e.g., cottons, linens, permanent press). The wash loads used in calculating the in-home percentage split between adaptive and manual cycle usage should be only those wash loads which conform to the definition of the energy test cycle.

Calculate:

T=The total number of energy test cycles run during the field test

T_a=The total number of adaptive control energy test cycles

T_m=The total number of manual control energy test cycles

The percentage weighting factors:

P_a=(T_a/T)×100 (the percentage weighting for adaptive control selection)

P_m=(T_m/T)×100 (the percentage weighting for manual control selection)

Energy consumption (HE_T, ME_T, and D_E) and water consumption (Q_T), values calculated in section 4 for the manual and adaptive modes, should be combined using P_a and P_m as the weighting factors.

[62 FR 45508, Aug. 27, 1997; 63 FR 16669, Apr. 6, 1998, as amended at 66 FR 3330, Jan. 12, 2001; 68 FR 62204, Oct. 31, 2003; 69 FR 18803, Apr. 9, 2004]

1. DEFINITIONS

2. TESTING CONDITIONS

2.1  Test room requirements.

2.2  Test unit installation requirements.

2.2.1  Defrost control settings.

2.2.2  Special requirements for units having a multiple-speed outdoor fan.

2.2.3  Special requirements for multi-split air conditioners and heat pumps, and systems composed of multiple mini-split units (outdoor units located side-by-side) that would normally operate using two or more indoor thermostats.

2.2.4  Wet-bulb temperature requirements for the air entering the indoor and outdoor coils.

2.2.4.1  Cooling mode tests.

2.2.4.2  Heating mode tests.

2.2.5  Additional refrigerant charging requirements.

2.3  Indoor air volume rates.

2.3.1  Cooling tests.

2.3.2  Heating tests.

2.4  Indoor coil inlet and outlet duct connections.

2.4.1  Outlet plenum for the indoor unit.

2.4.2  Inlet plenum for the indoor unit.

2.5  Indoor coil air property measurements and air damper box applications.

2.5.1  Test set-up on the inlet side of the indoor coil: For cases where the inlet damper box is installed.

2.5.1.1  If the section 2.4.2 inlet plenum is installed.

2.5.1.2  If the section 2.4.2 inlet plenum is not installed.

2.5.2  Test set-up on the inlet side of the indoor unit: For cases where no inlet damper box is installed.

2.5.3  Indoor coil static pressure difference measurement.

2.5.4  Test set-up on the outlet side of the indoor coil.

2.5.4.1  Outlet air damper box placement and requirements.

2.5.4.2  Procedures to minimize temperature maldistribution.

2.5.5  Dry bulb temperature measurement.

2.5.6  Water vapor content measurement.

2.5.7  Air damper box performance requirements.

2.6  Airflow measuring apparatus.

2.7  Electrical voltage supply.

2.8  Electrical power and energy measurements.

2.9  Time measurements.

2.10  Test apparatus for the secondary space conditioning capacity measurement.

2.10.1  Outdoor Air Enthalpy Method.

2.10.2  Compressor Calibration Method.

2.10.3  Refrigerant Enthalpy Method.

2.11  Measurement of test room ambient conditions.

2.12  Measurement of indoor fan speed.

2.13  Measurement of barometric pressure.

3. TESTING PROCEDURES

3.1  General Requirements.

3.1.1  Primary and secondary test methods.

3.1.2  Manufacturer-provided equipment overrides.

3.1.3  Airflow through the outdoor coil.

3.1.4  Airflow through the indoor coil.

3.1.4.1  Cooling Certified Air Volume Rate.

3.1.4.1.1  Cooling Certified Air Volume Rate for Ducted Units.

3.1.4.1.2  Cooling Certified Air Volume Rate for Non-ducted Units.

3.1.4.2  Cooling Minimum Air Volume Rate.

3.1.4.3  Cooling Intermediate Air Volume Rate.

3.1.4.4  Heating Certified Air Volume Rate.

3.1.4.4.1  Ducted heat pumps where the Heating and Cooling Certified Air Volume Rates are the same.

3.1.4.4.2  Ducted heat pumps where the Heating and Cooling Certified Air Volume Rates are different due to indoor fan operation.

3.1.4.4.3  Ducted heating-only heat pumps.

3.1.4.4.4  Non-ducted heat pumps, including non-ducted heating-only heat pumps.

3.1.4.5  Heating Minimum Air Volume Rate.

3.1.4.6  Heating Intermediate Air Volume Rate.

3.1.4.7  Heating Nominal Air Volume Rate.

3.1.5  Indoor test room requirement when the air surrounding the indoor unit is not supplied from the same source as the air entering the indoor unit.

3.1.6  Air volume rate calculations.

3.1.7  Test sequence.

3.1.8  Requirement for the air temperature distribution leaving the indoor coil.

3.1.9  Control of auxiliary resistive heating elements.

3.2  Cooling mode tests for different types of air conditioners and heat pumps.

3.2.1  Tests for a unit having a single-speed compressor that is tested with a fixed-speed indoor fan installed, with a constant-air-volume-rate indoor fan installed, or with no indoor fan installed.

3.2.2  Tests for a unit having a single-speed compressor and a variable-speed variable-air-volume-rate indoor fan installed.

3.2.2.1  Indoor fan capacity modulation that correlates with the outdoor dry bulb temperature.

3.2.2.2  Indoor fan capacity modulation based on adjusting the sensible to total (S/T) cooling capacity ratio.

3.2.3  Tests for a unit having a two-capacity compressor.

3.2.4  Tests for a unit having a variable-speed compressor.

3.3  Test procedures for steady-state wet coil cooling mode tests (the A, A₂, A₁, B, B₂, B₁, E_V, and F₁ Tests).

3.4  Test procedures for the optional steady-state dry coil cooling mode tests (the C, C₁, and G₁ Tests).

3.5  Test procedures for the optional cyclic dry coil cooling mode tests (the D, D₁, and I₁ Tests).

3.5.1  Procedures when testing ducted systems.

3.5.2  Procedures when testing non-ducted systems.

3.5.3  Cooling mode cyclic degradation coefficient calculation.

3.6  Heating mode tests for different types of heat pumps, including heating-only heat pumps.

3.6.1  Tests for a heat pump having a single-speed compressor that is tested with a fixed speed indoor fan installed, with a constant-air-volume-rate indoor fan installed, or with no indoor fan installed.

3.6.2  Tests for a heat pump having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor fan: capacity modulation correlates with outdoor dry bulb temperature.

3.6.3  Tests for a heat pump having a two-capacity compressor (see Definition 1.45), including two-capacity, northern heat pumps (see Definition 1.46).

3.6.4  Tests for a heat pump having a variable-speed compressor.

3.6.5  Additional test for a heat pump having a heat comfort controller.

3.7  Test procedures for steady-state Maximum Temperature and High Temperature heating mode tests (the H0₁, H1, H1₂, H1₁, and H1_N Tests).

3.8  Test procedures for the optional cyclic heating mode tests (the H0C₁, H1C, and H1C₁ Tests).

3.8.1  Heating mode cyclic degradation coefficient calculation.

3.9  Test procedures for Frost Accumulation heating mode tests (the H₂, H2₂, H2_V, and H2₁ Tests).

3.9.1  Average space heating capacity and electrical power calculations.

3.9.2  Demand defrost credit.

3.10  Test procedures for steady-state Low Temperature heating mode tests (the H₃, H3₂, and H3₁ Tests).

3.11  Additional requirements for the secondary test methods.

3.11.1  If using the Outdoor Air Enthalpy Method as the secondary test method.

3.11.1.1  If a preliminary test precedes the official test

3.11.1.2  If a preliminary test does not precede the official test.

3.11.1.3  Official test.

3.11.2  If using the Compressor Calibration Method as the secondary test method.

3.11.3  If using the Refrigerant Enthalpy Method as the secondary test method.

3.12  Rounding of space conditioning capacities for reporting purposes.

4. CALCULATIONS OF SEASONAL PERFORMANCE DESCRIPTORS

4.1  Seasonal Energy Efficiency Ratio (SEER) Calculations.

4.1.1  SEER calculations for an air conditioner or heat pump having a single-speed compressor that was tested with a fixed-speed indoor fan installed, a constant-air-volume-rate indoor fan installed, or with no indoor fan installed.

4.1.2  SEER calculations for an air conditioner or heat pump having a single-speed compressor and a variable-speed variable-air-volume-rate indoor fan.

4.1.2.1  Units covered by section 3.2.2.1 where indoor fan capacity modulation correlates with the outdoor dry bulb temperature.

4.1.2.2  Units covered by section 3.2.2.2 where indoor fan capacity modulation is used to adjust the sensible to total cooling capacity ratio.

4.1.3  SEER calculations for an air conditioner or heat pump having a two-capacity compressor.

4.1.3.1  Steady-state space cooling capacity at low compressor capacity is greater than or equal to the building cooling load at temperature T_j, Q _ck=1(T_j) ≥ BL(T_j).

4.1.3.2  Unit alternates between high (k=2) and low (k=1) compressor capacity to satisfy the building cooling load at temperature T_j, Q _ck=1(T_j) < BL(T_j) < Q _ck=2(T_j).

4.1.3.3  Unit only operates at high (k=2) compressor capacity at temperature T_j and its capacity is greater than the building cooling load, BL(T_j) < Q _ck=2(T_j).

4.1.3.4  Unit must operate continuously at high (k=2) compressor capacity at temperature T_j, BL(T_j) ≥ Q _ck=2(T_j).

4.1.4  SEER calculations for an air conditioner or heat pump having a variable-speed compressor.

4.1.4.1  Steady-state space cooling capacity when operating at minimum compressor speed is greater than or equal to the building cooling load at temperature T_j, Q _ck=1(T_j) ≥ BL(T_j).

4.1.4.2  Unit operates at an intermediate compressor speed (k=i) in order to match the building cooling load at temperature T_j, Q _ck=1(T_j) < BL(T_j) < Q _ck=2(T_j).

4.1.4.3  Unit must operate continuously at maximum (k=2) compressor speed at temperature T_j, BL(T_j) ≥ Q _ck=2(T_j).

4.2  Heating Seasonal Performance Factor (HSPF) Calculations.

4.2.1  Additional steps for calculating the HSPF of a heat pump having a single-speed compressor that was tested with a fixed-speed indoor fan installed, a constant-air-volume-rate indoor fan installed, or with no indoor fan installed.

4.2.2  Additional steps for calculating the HSPF of a heat pump having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor fan.

4.2.3  Additional steps for calculating the HSPF of a heat pump having a two-capacity compressor.

4.2.3.1  Steady-state space heating capacity when operating at low compressor capacity is greater than or equal to the building heating load at temperature T_j, Q _hk=1(T_j) ≥ BL(T_j).

4.2.3.2  Heat pump alternates between high (k=2) and low (k=1) compressor capacity to satisfy the building heating load at a temperature T_j, Q _hk=1(T_j) BL (T_j) < Q _hk=2(T_j).

4.2.3.3  Heat pump only operates at high (k=2) compressor capacity at temperature T_j and its capacity is greater than the building heating load, BL(T_j) < Q _hk=2(T_j).

4.2.3.4  Heat pump must operate continuously at high (k=2) compressor capacity at temperature T_j, BL(T_j) ≥ Q _hk=2(T_j).

4.2.4  Additional steps for calculating the HSPF of a heat pump having a variable-speed compressor.

4.2.4.1  Steady-state space heating capacity when operating at minimum compressor speed is greater than or equal to the building heating load at temperature T_j, Q _hk=1(T_j) ≥ BL(T_j).

4.2.4.2  Heat pump operates at an intermediate compressor speed (k=i) in order to match the building heating load at a temperature T_j, Q _hk=1(T_j) < BL(T_j) < Q _hk=2(T_j).

4.2.4.3  Heat pump must operate continuously at maximum (k=2) compressor speed at temperature T_j, BL(T_j) ≥ Q _hk=2(T_j).

4.2.5  Heat pumps having a heat comfort controller.

4.2.5.1  Heat pump having a heat comfort controller: Additional steps for calculating the HSPF of a heat pump having a single-speed compressor that was tested with a fixed-speed indoor fan installed, a constant-air-volume-rate indoor fan installed, or with no indoor fan installed.

4.2.5.2  Heat pump having a heat comfort controller: Additional steps for calculating the HSPF of a heat pump having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor fan.

4.2.5.3  Heat pumps having a heat comfort controller: Additional steps for calculating the HSPF of a heat pump having a two-capacity compressor.

4.2.5.4  Heat pumps having a heat comfort controller: Additional steps for calculating the HSPF of a heat pump having a variable-speed compressor. [Reserved]

4.3  Calculations of the Actual and Representative Regional Annual Performance Factors for Heat Pumps.

4.3.1  Calculation of actual regional annual performance factors (APF_A) for a particular location and for each standardized design heating requirement.

4.3.2  Calculation of representative regional annual performance factors (APF_R) for each generalized climatic region and for each standardized design heating requirement.

4.4  Rounding of SEER, HSPF, and APF for reporting purposes.

1. Definitions

1.1  Annual performance factor means the total heating and cooling done by a heat pump in a particular region in one year divided by the total electric energy used in one year. Paragraph (m)(3)(iii) of §430.23 of the Code of Federal Regulations states the calculation requirements for this rating descriptor.

1.2  ARI means Air-Conditioning and Refrigeration Institute.

1.3  ARI Standard 210/240–2003 means the test standard “Unitary Air-Conditioning and Air-Source Heat Pump Equipment” published in 2003 by ARI.

1.4  ASHRAE means the American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc.

1.5  ASHRAE Standard 23–93 means the test standard “Methods of Testing for Rating Positive Displacement Refrigerant Compressors and Condensing Units” published in 1993 by ASHRAE.

1.6  ASHRAE Standard 37–88 means the test standard “Methods of Testing for Rating Unitary Air-Conditioning and Heat Pump Equipment” published in 1988 by ASHRAE.

1.7  ASHRAE Standard 41.1–86 (RA 01) means the test standard “Standard Method for Temperature Measurement” published in 1986 and reaffirmed in 2001 by ASHRAE.

1.8  ASHRAE Standard 41.2–87 (RA 92) means the test standard “Standard Methods for Laboratory Airflow Measurement” published in 1987 and reaffirmed in 1992 by ASHRAE.

1.9  ASHRAE Standard 41.6–94 (RA 01) means the test standard “Method for Measurement of Moist Air Properties” published in 1994 and reaffirmed in 2001 by ASHRAE.

1.10  ASHRAE Standard 41.9–00 means the test standard “Calorimeter Test Methods for Mass Flow Measurements of Volatile Refrigerants” published in 2000 by ASHRAE.

1.11  ASHRAE Standard 51–99/AMCA Standard 210–1999 means the test standard “Laboratory Methods of Testing Fans for Aerodynamic Performance Rating” published in 1999 by ASHRAE and the Air Movement and Control Association International, Inc.

1.12  ASHRAE Standard 116–95 means the test standard “Methods of Testing for Rating for Seasonal Efficiency of Unitary Air Conditioners and Heat Pumps” published in 1995 by ASHRAE.

1.13  CFR means Code of Federal Regulations.

1.14  Constant-air-volume-rate indoor fan means a fan that varies its operating speed to provide a fixed air-volume-rate from a ducted system.

1.15  Continuously recorded, when referring to a dry bulb measurement, means that the specified temperature must be sampled at regular intervals that are equal to or less than the maximum intervals specified in section 4.3 part “a” of ASHRAE Standard 41.1–86 (RA 01). If such dry bulb temperatures are used only for test room control, it means that one samples at regular intervals equal to or less than the maximum intervals specified in section 4.3 part “b” of the same ASHRAE Standard. Regarding wet bulb temperature, dew point temperature, or relative humidity measurements, continuously recorded means that the measurements must be made at regular intervals that are equal to or less than 1 minute.

1.16  Cooling load factor (CLF) means the ratio having as its numerator the total cooling delivered during a cyclic operating interval consisting of one ON period and one OFF period. The denominator is the total cooling that would be delivered, given the same ambient conditions, had the unit operated continuously at its steady-state space cooling capacity for the same total time (ON + OFF) interval.

1.17  Coefficient of Performance (COP) means the ratio of the average rate of space heating delivered to the average rate of electrical energy consumed by the heat pump. These rate quantities must be determined from a single test or, if derived via interpolation, must be tied to a single set of operating conditions. COP is a dimensionless quantity. When determined for a ducted unit tested without an indoor fan installed, COP must include the section 3.7, 3.8, and 3.9.1 default values for the heat output and power input of a fan motor.

1.18  Cyclic Test means a test where the unit's compressor is cycled on and off for specific time intervals. A cyclic test provides half the information needed to calculate a degradation coefficient.

1.19  Damper box means a short section of duct having an air damper that meets the performance requirements of section 2.5.7.

1.20  Degradation coefficient (C_D) means a parameter used in calculating the part load factor. The degradation coefficient for cooling is denoted by C_D^c . The degradation coefficient for heating is denoted by C_D^h .

1.21  Demand-defrost control system means a system that defrosts the heat pump outdoor coil only when measuring a predetermined degradation of performance. The heat pump's controls monitor one or more parameters that always vary with the amount of frost accumulated on the outdoor coil (e.g., coil to air differential temperature, coil differential air pressure, outdoor fan power or current, optical sensors, etc.) at least once for every ten minutes of compressor ON-time when space heating. One acceptable alternative to the criterion given in the prior sentence is a feedback system that measures the length of the defrost period and adjusts defrost frequency accordingly.¹ In all cases, when the frost parameter(s) reaches a predetermined value, the system initiates a defrost. In a demand-defrost control system, defrosts are terminated based on monitoring a parameter(s) that indicates that frost has been eliminated from the coil.

A demand-defrost control system, which otherwise meets the above requirements, may allow time-initiated defrosts if, and only if, such defrosts occur after 6 hours of compressor operating time.

1.22  Design heating requirement (DHR) predicts the space heating load of a residence when subjected to outdoor design conditions. Estimates for the minimum and maximum DHR are provided for six generalized U.S. climatic regions in section 4.2.

1.23  Dry-coil tests are cooling mode tests where the wet-bulb temperature of the air supplied to the indoor coil is maintained low enough that no condensate forms on this coil.

1.24  Ducted system means an air conditioner or heat pump that is designed to be permanently installed equipment and delivers conditioned air to the indoor space through a duct(s). The air conditioner or heat pump may be either a split system or a single-packaged unit.

1.25  Energy efficiency ratio (EER) means the ratio of the average rate of space cooling delivered to the average rate of electrical energy consumed by the air conditioner or heat pump. These rate quantities must be determined from a single test or, if derived via interpolation, must be tied to a single set of operating conditions. EER is expressed in units of

When determined for a ducted unit tested without an indoor fan installed, EER must include the section 3.3 and 3.5.1 default values for the heat output and power input of a fan motor.

1.26  Heating load factor (HLF) means the ratio having as its numerator the total heating delivered during a cyclic operating interval consisting of one ON period and one OFF period. The denominator is the total heating that would be delivered, given the same ambient conditions, if the unit operated continuously at its steady-state space heating capacity for the same total time (ON plus OFF) interval.

1.27  Heating seasonal performance factor (HSPF) means the total space heating required during the space heating season, expressed in Btu's, divided by the total electrical energy consumed by the heat pump system during the same season, expressed in watt-hours. The HSPF used to evaluate compliance with the Energy Conservation Standards (see 10 CFR 430.32(c), Subpart C) is based on Region IV, the minimum standardized design heating requirement, and the sampling plan stated in 10 CFR 430.24(m), Subpart B.

1.28  Heat pump having a heat comfort controller means equipment that regulates the operation of the electric resistance elements to assure that the air temperature leaving the indoor section does not fall below a specified temperature. This specified temperature is usually field adjustable. Heat pumps that actively regulate the rate of electric resistance heating when operating below the balance point (as the result of a second stage call from the thermostat) but do not operate to maintain a minimum delivery temperature are not considered as having a heat comfort controller.

1.29  Mini-split air conditioners and heat pumps means systems that have a single outdoor section and one or more indoor sections. The indoor sections cycle on and off in unison in response to a single indoor thermostat.

1.30  Multiple-split air conditioners and heat pumps means systems that have two or more indoor sections. The indoor sections operate independently and can be used to condition multiple zones in response to multiple indoor thermostats.

1.31  Non-ducted system means an air conditioner or heat pump that is designed to be permanently installed equipment and directly heats or cools air within the conditioned space using one or more indoor coils that are mounted on room walls and/or ceilings. The unit may be of a modular design that allows for combining multiple outdoor coils and compressors to create one overall system. Non-ducted systems covered by this test procedure are all split systems.

1.32  Part-load factor (PLF) means the ratio of the cyclic energy efficiency ratio (coefficient of performance) to the steady-state energy efficiency ratio (coefficient of performance). Evaluate both energy efficiency ratios (coefficients of performance) based on operation at the same ambient conditions.

1.33  Seasonal energy efficiency ratio (SEER) means the total heat removed from the conditioned space during the annual cooling season, expressed in Btu's, divided by the total electrical energy consumed by the air conditioner or heat pump during the same season, expressed in watt-hours. The SEER calculation in section 4.1 of this Appendix and the sampling plan stated in 10 CFR Subpart B, 430.24(m) are used to evaluate compliance with the Energy Conservation Standards. (See 10 CFR 430.32(c), Subpart C.)

1.34  Single-packaged unit means any central air conditioner or heat pump that has all major assemblies enclosed in one cabinet.

1.35  Small-duct, high-velocity system means a system that contains a blower and indoor coil combination that is designed for, and produces, at least 1.2 inches (of water) of external static pressure when operated at the certified air volume rate of 220–350 cfm per rated ton of cooling. When applied in the field, small-duct products use high-velocity room outlets (i.e., generally greater than 1000 fpm) having less than 6.0 square inches of free area.

1.36  Split system means any air conditioner or heat pump that has one or more of the major assemblies separated from the others.

1.37  Standard Air means dry air at 70 °F and 14.696 psia. Under these conditions, dry air has a mass density of 0.075 lb/ft³ .

1.38  Steady-state test means a test where the test conditions are regulated to remain as constant as possible while the unit operates continuously in the same mode.

1.39  Temperature bin means the 5 °F increments that are used to partition the outdoor dry-bulb temperature ranges of the cooling (≥ 65°F) and heating (<65°F) seasons.

1.40  Test condition tolerance means the maximum permissible difference between the average value of the measured test parameter and the specified test condition.

1.41  Test operating tolerance means the maximum permissible range that a measurement may vary over the specified test interval. The difference between the maximum and minimum sampled values must be less than or equal to the specified test operating tolerance.

1.42  Time adaptive defrost control system is a demand-defrost control system (see definition 1.21) that measures the length of the prior defrost period(s) and uses that information to automatically determine when to initiate the next defrost cycle.

1.43  Time-temperature defrost control systems initiate or evaluate initiating a defrost cycle only when a predetermined cumulative compressor ON-time is obtained. This predetermined ON-time is generally a fixed value (e.g., 30, 45, 90 minutes) although it may vary based on the measured outdoor dry-bulb temperature. The ON-time counter accumulates if controller measurements (e.g., outdoor temperature, evaporator temperature) indicate that frost formation conditions are present, and it is reset/remains at zero at all other times. In one application of the control scheme, a defrost is initiated whenever the counter time equals the predetermined ON-time. The counter is reset when the defrost cycle is completed.

In a second application of the control scheme, one or more parameters are measured (e.g., air and/or refrigerant temperatures) at the predetermined, cumulative, compressor ON-time. A defrost is initiated only if the measured parameter(s) falls within a predetermined range. The ON-time counter is reset regardless of whether a defrost is initiated. If systems of this second type use cumulative ON-time intervals of 10 minutes or less, then the heat pump may qualify as having a demand defrost control system (see definition 1.21).

1.44  Triple-split system means an air conditioner or heat pump that is composed of three separate components: An outdoor fan coil section, an indoor fan coil section, and an indoor compressor section.

1.45  Two-capacity (or two-stage) compressor means an air conditioner or heat pump that has one of the following:

(1) A two-speed compressor,

(2) Two compressors where only one compressor ever operates at a time,

(3) Two compressors where one compressor (Compressor #1) operates at low loads and both compressors (Compressors #1 and #2) operate at high loads but Compressor #2 never operates alone, or

(4) A compressor that is capable of cylinder or scroll unloading.

For such systems, low capacity means:

(1) Operating at low compressor speed,

(2) Operating the lower capacity compressor,

(3) Operating Compressor #1, or

(4) Operating with the compressor unloaded (e.g., operating one piston of a two-piston reciprocating compressor, using a fixed fractional volume of the full scroll, etc.).

For such systems, high capacity means:

(1) Operating at high compressor speed,

(2) Operating the higher capacity compressor,

(3) Operating Compressors #1 and #2, or

(4) Operating with the compressor loaded (e.g., operating both pistons of a two-piston reciprocating compressor, using the full volume of the scroll).

1.46  Two-capacity, northern heat pump means a heat pump that has a factory or field-selectable lock-out feature to prevent space cooling at high-capacity. Two-capacity heat pumps having this feature will typically have two sets of ratings, one with the feature disabled and one with the feature enabled. The indoor coil model number should reflect whether the ratings pertain to the lockout enabled option via the inclusion of an extra identifier, such as “+LO.” When testing as a two-capacity, northern heat pump, the lockout feature must remain enabled for all tests.

1.47  Wet-coil test means a test conducted at test conditions that typically cause water vapor to condense on the test unit evaporator coil.

2. Testing Conditions

This test procedure covers split-type and single-packaged ducted units and split-type non-ducted units. Except for units having a variable-speed compressor, ducted units tested without an indoor fan installed are covered.

a. Only a subset of the sections listed in this test procedure apply when testing and rating a particular unit. Tables 1–A through 1–C show which sections of the test procedure apply to each type of equipment. In each table, look at all four of the Roman numeral categories to see what test sections apply to the equipment being tested.

1. The first category, Rows I–1 through I–4 of the Tables, pertains to the compressor and indoor fan features of the equipment. After identifying the correct “I” row, find the table cells in the same row that list the type of equipment being tested: Air conditioner (AC), heat pump (HP), or heating-only heat pump (HH). Use the test section(s) listed above each noted table cell for testing and rating the unit.

2. The second category, Rows II–1 and II–2, pertains to the presence or absence of ducts. Row II–1 shows the test procedure sections that apply to ducted systems, and Row II–2 shows those that apply to non-ducted systems.

3. The third category is for special features that may be present in the equipment. When testing units that have one or more of the three (special) equipment features described by the Table legend for Category III, use Row III to find test sections that apply.

4. The fourth category is for the secondary test method to be used. If the secondary method for determining the unit's cooling and/or heating capacity is known, use Row IV to find the appropriate test sections. Otherwise, include all of the test sections referenced by Row IV cell entries—i.e., sections 2.10 to 2.10.3 and 3.11 to 3.11.3—among those sections consulted for testing and rating information.

b. Obtain a complete listing of all pertinent test sections by recording those sections identified from the four categories above.

c. The user should note that, for many sections, only part of a section applies to the unit being tested. In a few cases, the entire section may not apply. For example, sections 3.4 to 3.5.3 (which describe optional dry coil tests), are not relevant if the allowed default value for the cooling mode cyclic degradation coefficient is used rather than determining it by testing.

Example for Using Tables 1–A to 1–C

Equipment Description: A ducted air conditioner having a single-speed compressor, a fixed-speed indoor fan, and a multi-speed outdoor fan.

Secondary Test Method: Refrigerant Enthalpy Method

Step 1. Determine which of four listed Row “I” options applies ==> Row I–2

Table 1–A: “AC” in Row I–2 is found in the columns for sections 1.1 to 1.47, 2.1 to 2.2, 2.2.4 to 2.2.4.1, 2.2.5, 2.3 to 2.3.1, 2.4 to 2.4.1, 2.5, 2.5.2 to 2.10, and 2.11 to 2.13.

Table 1–B: “AC” is listed in Row I–2 for sections 3 to 3.1.4, 3.1.5 to 3.1.8, 3.2.1, 3.3 to 3.5, 3.5.3, 3.11 and 3.12.

Table 1–C: “AC” is listed in Row I–2 for sections 4.1.1 and 4.4.

Step 2. Equipment is ducted ==> Row II–1

Table 1–A: “AC” is listed in Row II–1 for sections 2.4.2 and 2.5.1 to 2.5.1.2.

Table 1–B: “AC” is listed in Row II–1 for sections 3.1.4.1 to 3.1.4.1.1 and 3.5.1.

Table 1–C: no “AC” listings in Row II–1.

Step 3. Equipment Special Features include multi-speed outdoor fan ==> Row III, M

Table 1–A: “M” is listed in Row III for section 2.2.2

Tables 1–B and 1–C: no “M” listings in Row III.

Step 4. Secondary Test Method is Refrigerant Enthalpy Method ==> Row IV, R

Table 1–A: “R” is listed in Row IV for section 2.10.3

Table 1–B: “R” is listed in Row IV for section 3.11.3

Table 1–C: no “R” listings in Row IV.

Step 5. Cumulative listing of applicable test procedure sections 1.1 to 1.47, 2.1 to 2.2, 2.2.2, 2.2.4 to 2.4.1, 2.2.5, 2.3 to 2.3.1, 2.4 to 2.4.1, 2.4.2, 2.5, 2.5.1 to 2.5.1.2, 2.5.2 to 2.10, 2.10.3, 2.11 to 2.13, 3. to 3.1.4, 3.1.4.1 to 3.1.4.1.1, 3.1.5 to 3.1.8, 3.2.1, 3.3 to 3.5, 3.5.1, 3.5.3, 3.11, 3.11.3, 3.12, 4.1.1, and 4.4.

2.1  Test room requirements. a. Test using two side-by-side rooms, an indoor test room and an outdoor test room. These rooms must comply with the requirements specified in sections 8.1.2 and 8.1.3 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22).

b. Inside these test rooms, use artificial loads during cyclic tests and frost accumulation tests, if needed, to produce stabilized room air temperatures. For one room, select an electric resistance heater(s) having a heating capacity that is approximately equal to the heating capacity of the test unit's condenser. For the second room, select a heater(s) having a capacity that is close to the sensible cooling capacity of the test unit's evaporator. When applied, cycle the heater located in the same room as the test unit evaporator coil ON and OFF when the test unit cycles ON and OFF. Cycle the heater located in the same room as the test unit condensing coil ON and OFF when the test unit cycles OFF and ON.

2.2  Test unit installation requirements. a. Install the unit according to section 8.6 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). With respect to interconnecting tubing used when testing split systems, however, follow the requirements given in section 6.1.3.5 of ARI Standard 210/240–2003 (incorporated by reference, see §430.22). When testing triple-split systems (see Definition 1.44), use the tubing length specified in section 6.1.3.5 of ARI Standard 210/240–2003 (incorporated by reference, see §430.22) to connect the outdoor coil, indoor compressor section, and indoor coil while still meeting the requirement of exposing 10 feet of the tubing to outside conditions. When testing non-ducted systems having multiple indoor coils, connect each indoor fan-coil to the outdoor unit using: a. 25 feet of tubing, or b. tubing furnished by the manufacturer, whichever is longer. If they are needed to make a secondary measurement of capacity, install refrigerant pressure measuring instruments as described in section 8.6.5 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). Refer to section 2.10 of this Appendix to learn which secondary methods require refrigerant pressure measurements. At a minimum, insulate the low pressure line(s) of a split system with foam insulation having an inside diameter that matches the refrigerant tubing and a nominal thickness of 1/2 inch.

b. For units designed for both horizontal and vertical installation or for both up-flow and down-flow vertical installations, the manufacturer must specify the orientation used for testing. Conduct testing with the following installed:

(1) The most restrictive filter(s);

(2) Supplementary heating coils; and

(3) Other equipment specified as part of the unit, including all hardware used by a heat comfort controller if so equipped (see Definition 1.28).

c. Testing a ducted unit without having an indoor air filter installed is permissible as long as the minimum external static pressure requirement is adjusted as stated in Table 2, note 3 (see section 3.1.4). Except as noted in section 3.1.9, prevent the indoor air supplementary heating coils from operating during all tests. For coil-only indoor units that are supplied without an enclosure, create an enclosure using 1 inch fiberglass ductboard having a nominal density of 6 pounds per cubic foot. Or alternatively, use some other insulating material having a thermal resistance (“R” value) between 4 and 6 hr·ft² · °F/Btu. For units where the coil is housed within an enclosure or cabinet, no extra insulating or sealing is allowed.

2.2.1  Defrost control settings. Set heat pump defrost controls at the normal settings which most typify those encountered in generalized climatic region IV. (Refer to Figure 2 and Table 17 of section 4.2 for information on region IV.) For heat pumps that use a time-adaptive defrost control system (see Definition 1.42), the manufacturer must specify the frosting interval to be used during Frost Accumulation tests and provide the procedure for manually initiating the defrost at the specified time. To ease testing of any unit, the manufacturer should provide information and any necessary hardware to manually initiate a defrost cycle.

2.2.2  Special requirements for units having a multiple-speed outdoor fan. Configure the multiple-speed outdoor fan according to the manufacturer's specifications, and thereafter, leave it unchanged for all tests. The controls of the unit must regulate the operation of the outdoor fan during all lab tests except dry coil cooling mode tests. For dry coil cooling mode tests, the outdoor fan must operate at the same speed used during the required wet coil test conducted at the same outdoor test conditions.

2.2.3  Special requirements for multi-split air conditioners and heat pumps, and systems composed of multiple mini-split units (outdoor units located side-by-side) that would normally operate using two or more indoor thermostats. During the steady-state tests, shunt all thermostats to make all indoor fan-coil units operate simultaneously. To ease the testing burden of cyclic tests, consider creating a single control circuit that allows simultaneous cycling of all compressor systems. For these systems, the test procedure references to a single indoor fan, outdoor fan, and compressor means all indoor fans, all outdoor fans, and all compressor systems.

2.2.4  Wet-bulb temperature requirements for the air entering the indoor and outdoor coils.

2.2.4.1  Cooling mode tests. For wet-coil cooling mode tests, regulate the water vapor content of the air entering the indoor unit to the applicable wet-bulb temperature listed in Tables 3 to 6. As noted in these same tables, achieve a wet-bulb temperature during dry-coil cooling mode tests that results in no condensate forming on the indoor coil. Controlling the water vapor content of the air entering the outdoor side of the unit is not required for cooling mode tests except when testing:

(1) Units that reject condensate to the outdoor coil during wet coil tests. Tables 3–6 list the applicable wet-bulb temperatures.

(2) Single-packaged units where all or part of the indoor section is located in the outdoor test room. The average dew point temperature of the air entering the outdoor coil during wet coil tests must be within ±3.0 °F of the average dew point temperature of the air entering the indoor coil over the 30-minute data collection interval described in section 3.3. For dry coil tests on such units, it may be necessary to limit the moisture content of the air entering the outdoor side of the unit to meet the requirements of section 3.4.

2.2.4.2  Heating mode tests. For heating mode tests, regulate the water vapor content of the air entering the outdoor unit to the applicable wet-bulb temperature listed in Tables 9 to 12. The wet-bulb temperature entering the indoor side of the heat pump must not exceed 60 °F. Additionally, if the Outdoor Air Enthalpy test method is used while testing a single-packaged heat pump where all or part of the outdoor section is located in the indoor test room, adjust the wet-bulb temperature for the air entering the indoor side to yield an indoor-side dew point temperature that is as close as reasonably possible to the dew point temperature of the outdoor-side entering air.

2.2.5  Additional refrigerant charging requirements. Charging according to the “manufacturer's instructions,” as stated in section 8.6 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22), means the manufacturer's installation instructions that come packaged with the unit. If a unit requires charging but the installation instructions do not specify a charging procedure, then evacuate the unit and add the nameplate refrigerant charge. Where the manufacturer's installation instructions contain two sets of refrigerant charging criteria, one for field installations and one for lab testing, use the field installation criteria. For third-party testing, the test laboratory may consult with the manufacturer about the refrigerant charging procedure and make any needed corrections so long as they do not contradict the published installation instructions. The manufacturer may specify an alternative charging criteria to the third-party laboratory so long as the manufacturer thereafter revises the published installation instructions accordingly.

2.3  Indoor air volume rates. If a unit's controls allow for overspeeding the indoor fan (usually on a temporary basis), take the necessary steps to prevent overspeeding during all tests.

2.3.1  Cooling tests. a. Set indoor fan control options (e.g., fan motor pin settings, fan motor speed) according to the published installation instructions that are provided with the equipment while meeting the airflow requirements that are specified in sections 3.1.4.1 to 3.1.4.3.

b. Express the Cooling Certified Air Volume Rate, the Cooling Minimum Air Volume Rate, and the Cooling Intermediate Air Volume Rate in terms of standard air.

2.3.2  Heating tests. a. If needed, set the indoor fan control options (e.g., fan motor pin settings, fan motor speed) according to the published installation instructions that are provided with the equipment. Do this set-up while meeting all applicable airflow requirements specified in sections 3.1.4.4 to 3.1.4.7.

b. Express the Heating Certified Air Volume Rate, the Heating Minimum Air Volume Rate, the Heating Intermediate Air Volume Rate, and the Heating Nominal Air Volume Rate in terms of standard air.

2.4  Indoor coil inlet and outlet duct connections. Insulate and/or construct the outlet plenum described in section 2.4.1 and, if installed, the inlet plenum described in section 2.4.2 with thermal insulation having a nominal overall sistance (R-value) of at least 19 hr·ft² · °F/Btu.

2.4.1  Outlet plenum for the indoor unit. Attach a plenum to the outlet of the indoor coil. (Note: for some packaged systems, the indoor coil may be located in the outdoor test room.) For non-ducted systems having multiple indoor coils, attach a plenum to each indoor coil outlet. Add a static pressure tap to each face of the (each) outlet plenum, if rectangular, or at four evenly distributed locations along the circumference of an oval or round plenum. Create a manifold that connects the four static pressure taps. Figure 1 shows two of the three options allowed for the manifold configuration; the third option is the broken-ring, four-to-one manifold configuration that is shown in Figure 7 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). See Figures 7 and 8 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) for the cross-sectional dimensions and minimum length of the (each) plenum and the locations for adding the static pressure taps for units tested with and without an indoor fan installed. For a non-ducted system having multiple indoor coils, have all outlet plenums discharge air into a single common duct. At the plane where each plenum enters the common duct, install an adjustable airflow damper and use it to equalize the static pressure in each plenum.

2.4.2  Inlet plenum for the indoor unit. Install an inlet plenum when testing a coil-only indoor unit or a packaged system where the indoor coil is located in the outdoor test room. Add static pressure taps at the center of each face of this plenum, if rectangular, or at four evenly distributed locations along the circumference of an oval or round plenum. Make a manifold that connects the four static pressure taps using one of the three configurations specified in section 2.4.1. See Figure 8 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) for cross-sectional dimensions, the minimum length of the inlet plenum, and the locations of the static pressure taps. When testing a ducted unit having an indoor fan (and the indoor coil is in the indoor test room), the manufacturer has the option to test with or without an inlet plenum installed. Space limitations within the test room may dictate that the manufacturer choose the latter option. If used, construct the inlet plenum and add the four static pressure taps as shown in Figure 8 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). Manifold the four static pressure taps using one of the three configurations specified in section 2.4.1. Never use an inlet plenum when testing a non-ducted system.

2.5  Indoor coil air property measurements and air damper box applications. a. Measure the dry-bulb temperature and water vapor content of the air entering and leaving the indoor coil. If needed, use an air sampling device to divert air to a sensor(s) that measures the water vapor content of the air. See Figure 2 of ASHRAE Standard 41.1–86 (RA 01) (incorporated by reference, see §430.22) for guidance on constructing an air sampling device. The sampling device may also divert air to a remotely located sensor(s) that measures dry bulb temperature. The air sampling device and the remotely located temperature sensor(s) may be used to determine the entering air dry bulb temperature during any test. The air sampling device and the remotely located leaving air dry bulb temperature sensor(s) may be used for all tests except:

(1) Cyclic tests; and

(2) Frost accumulation tests.

b. An acceptable alternative in all cases, including the two special cases noted above, is to install a grid of dry bulb temperature sensors within the outlet and inlet ducts. Use a temperature grid to get the average dry bulb temperature at one location, leaving or entering, or when two grids are applied as a thermopile, to directly obtain the temperature difference. A grid of temperature sensors (which may also be used for determining average leaving air dry bulb temperature) is required to measure the temperature distribution within a cross-section of the leaving airstream.

c. Use an inlet and outlet air damper box when testing ducted systems if conducting one or both of the cyclic tests listed in sections 3.2 and 3.6. Otherwise, install an outlet air damper box when testing heat pumps, both ducted and non-ducted, that cycle off the indoor fan during defrost cycles if no other means is available for preventing natural or forced convection through the indoor unit when the indoor fan is off. Never use an inlet damper box when testing a non-ducted system.

2.5.1  Test set-up on the inlet side of the indoor coil: for cases where the inlet damper box is installed. a. Install the inlet side damper box as specified in section 2.5.1.1 or 2.5.1.2, whichever applies. Insulate or construct the ductwork between the point where the air damper is installed and where the connection is made to either the inlet plenum (section 2.5.1.1 units) or the indoor unit (section 2.5.1.2 units) with thermal insulation that has a nominal overall resistance (R-value) of at least 19 hr·ft² · °F/Btu.

b. Locate the grid of entering air dry-bulb temperature sensors, if used, at the inlet of the damper box. Locate the air sampling device, or the sensor used to measure the water vapor content of the inlet air, at a location immediately upstream of the damper box inlet.

2.5.1.1  If the section 2.4.2 inlet plenum is installed. Install the inlet damper box upstream of the inlet plenum. The cross-sectional flow area of the damper box must be equal to or greater than the flow area of the inlet plenum. If needed, use an adaptor plate or a transition duct section to connect the damper box with the inlet plenum.

2.5.1.2  If the section 2.4.2 inlet plenum is not installed. Install the damper box immediately upstream of the air inlet of the indoor unit. The cross-sectional dimensions of the damper box must be equal to or greater than the dimensions of the indoor unit inlet. If needed, use an adaptor plate or a short transition duct section to connect the damper box with the unit's air inlet. Add static pressure taps at the center of each face of the damper box, if rectangular, or at four evenly distributed locations along the circumference, if oval or round. Locate the pressure taps between the inlet damper and the inlet of the indoor unit. Make a manifold that connects the four static pressure taps.

2.5.2  Test set-up on the inlet side of the indoor unit: for cases where no inlet damper box is installed. If using the section 2.4.2 inlet plenum and a grid of dry bulb temperature sensors, mount the grid at a location upstream of the static pressure taps described in section 2.4.2, preferably at the entrance plane of the inlet plenum. If the section 2.4.2 inlet plenum is not used, but a grid of dry bulb temperature sensors is used, locate the grid approximately 6 inches upstream from the inlet of the indoor coil. Or, in the case of non-ducted units having multiple indoor coils, locate a grid approximately 6 inches upstream from the inlet of each indoor coil. Position an air sampling device, or the sensor used to measure the water vapor content of the inlet air, immediately upstream of the (each) entering air dry-bulb temperature sensor grid. If a grid of sensors is not used, position the entering air sampling device (or the sensor used to measure the water vapor content of the inlet air) as if the grid were present.

2.5.3  Indoor coil static pressure difference measurement. Section 6.4.4.1 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) describes the method for fabricating static pressure taps. Also refer to Figure 2A of ASHRAE Standard 51–99/AMCA Standard 210–99 (incorporated by reference, see §430.22). Use a differential pressure measuring instrument that is accurate to within ±0.01 inches of water and has a resolution of at least 0.01 inches of water to measure the static pressure difference between the indoor coil air inlet and outlet. Connect one side of the differential pressure instrument to the manifolded pressure taps installed in the outlet plenum. Connect the other side of the instrument to the manifolded pressure taps located in either the inlet plenum or incorporated within the air damper box. If an inlet plenum or inlet damper box are not used, leave the inlet side of the differential pressure instrument open to the surrounding atmosphere. For non-ducted systems that are tested with multiple outlet plenums, measure the static pressure within each outlet plenum relative to the surrounding atmosphere.

2.5.4  Test set-up on the outlet side of the indoor coil. a. Install an interconnecting duct between the outlet plenum described in section 2.4.1 and the airflow measuring apparatus described below in section 2.6. The cross-sectional flow area of the interconnecting duct must be equal to or greater than the flow area of the outlet plenum or the common duct used when testing non-ducted units having multiple indoor coils. If needed, use adaptor plates or transition duct sections to allow the connections. To minimize leakage, tape joints within the interconnecting duct (and the outlet plenum). Construct or insulate the entire flow section with thermal insulation having a nominal overall resistance (R-value) of at least 19 hr·ft² · °F/Btu.

b. Install a grid(s) of dry-bulb temperature sensors inside the interconnecting duct. Also, install an air sampling device, or the sensor(s) used to measure the water vapor content of the outlet air, inside the interconnecting duct. Locate the dry-bulb temperature grid(s) upstream of the air sampling device (or the in-duct sensor(s) used to measure the water vapor content of the outlet air). Air that circulates through an air sampling device and past a remote water-vapor-content sensor(s) must be returned to the interconnecting duct at a point:

(1) Downstream of the air sampling device;

(2) Upstream of the outlet air damper box, if installed; and

(3) Upstream of the section 2.6 airflow measuring apparatus.

2.5.4.1  Outlet air damper box placement and requirements. If using an outlet air damper box (see section 2.5), install it within the interconnecting duct at a location downstream of the location where air from the sampling device is reintroduced or downstream of the in-duct sensor that measures water vapor content of the outlet air. The leakage rate from the combination of the outlet plenum, the closed damper, and the duct section that connects these two components must not exceed 20 cubic feet per minute when a negative pressure of 1 inch of water column is maintained at the plenum's inlet.

2.5.4.2  Procedures to minimize temperature maldistribution. Use these procedures if necessary to correct temperature maldistributions. Install a mixing device(s) upstream of the outlet air, dry-bulb temperature grid (but downstream of the outlet plenum static pressure taps). Use a perforated screen located between the mixing device and the dry-bulb temperature grid, with a maximum open area of 40 percent. One or both items should help to meet the maximum outlet air temperature distribution specified in section 3.1.8. Mixing devices are described in sections 6.3—6.5 of ASHRAE Standard 41.1–86 (RA 01) (incorporated by reference, see §430.22) and section 5.2.2 of ASHRAE Standard 41.2–87 (RA 92) (incorporated by reference, see §430.22).

2.5.5  Dry bulb temperature measurement. a. Measure dry bulb temperatures as specified in sections 4, 5, 6.1–6.10, 9, 10, and 11 of ASHRAE Standard 41.1–86 (RA 01) (incorporated by reference, see §430.22). The transient testing requirements cited in section 4.3 of ASHRAE Standard 41.1–86 (RA 01) (incorporated by reference, see §430.22) apply if conducting a cyclic or frost accumulation test.

b. Distribute the sensors of a dry-bulb temperature grid over the entire flow area. The required minimum is 9 sensors per grid.

2.5.6  Water vapor content measurement. Determine water vapor content by measuring dry-bulb temperature combined with the air wet-bulb temperature, dew point temperature, or relative humidity. If used, construct and apply wet-bulb temperature sensors as specified in sections 4, 5, 6, 9, 10, and 11 of ASHRAE Standard 41.1–86 (RA 01) (incorporated by reference, see §430.22). As specified in ASHRAE 41.1–86 (RA 01) (incorporated by reference, see §430.22), the temperature sensor (wick removed) must be accurate to within ±0.2°F. If used, apply dew point hygrometers as specified in sections 5 and 8 of ASHRAE Standard 41.6–94 (RA 01) (incorporated by reference, see §430.22). The dew point hygrometers must be accurate to within ±0.4°F when operated at conditions that result in the evaluation of dew points above 35°F. If used, a relative humidity (RH) meter must be accurate to within ±0.7% RH. Other means to determine the psychrometric state of air may be used as long as the measurement accuracy is equivalent to or better than the accuracy achieved from using a wet-bulb temperature sensor that meets the above specifications.

2.5.7  Air damper box performance requirements. If used (see section 2.5), the air damper box(es) must be capable of being completely opened or completely closed within 10 seconds for each action.

2.6  Airflow measuring apparatus. a. Fabricate and operate an Air Flow Measuring Apparatus as specified in section 6.6 of ASHRAE Standard 116–95 (incorporated by reference, see §430.22). Refer to Figure 12 of ASHRAE Standard 51–99/AMCA Standard 210–99 (incorporated by reference, see §430.22) or Figure 14 of ASHRAE Standard 41.2–87 (RA 92) (incorporated by reference, see §430.22) for guidance on placing the static pressure taps and positioning the diffusion baffle (settling means) relative to the chamber inlet.

b. Connect the airflow measuring apparatus to the interconnecting duct section described in section 2.5.4. See sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2, and 4 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22), and Figures D1, D2, and D4 of ARI Standard 210/240–2003 (incorporated by reference, see §430.22) for illustrative examples of how the test apparatus may be applied within a complete laboratory set-up. Instead of following one of these examples, an alternative set-up may be used to handle the air leaving the airflow measuring apparatus and to supply properly conditioned air to the test unit's inlet. The alternative set-up, however, must not interfere with the prescribed means for measuring airflow rate, inlet and outlet air temperatures, inlet and outlet water vapor contents, and external static pressures, nor create abnormal conditions surrounding the test unit. (Note: Do not use an enclosure as described in section 6.1.3 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) when testing triple-split units.)

2.7  Electrical voltage supply. Perform all tests at the voltage specified in section 6.1.3.2 of ARI Standard 210/240–2003 (incorporated by reference, see §430.22) for “Standard Rating Tests.” Measure the supply voltage at the terminals on the test unit using a volt meter that provides a reading that is accurate to within ±1.0 percent of the measured quantity.

2.8  Electrical power and energy measurements. a. Use an integrating power (watt-hour) measuring system to determine the electrical energy or average electrical power supplied to all components of the air conditioner or heat pump (including auxiliary components such as controls, transformers, crankcase heater, integral condensate pump on non-ducted indoor units, etc.). The watt-hour measuring system must give readings that are accurate to within ±0.5 percent. For cyclic tests, this accuracy is required during both the ON and OFF cycles. Use either two different scales on the same watt-hour meter or two separate watt-hour meters. Activate the scale or meter having the lower power rating within 15 seconds after beginning an OFF cycle. Activate the scale or meter having the higher power rating active within 15 seconds prior to beginning an ON cycle. For ducted units tested with a fan installed, the ON cycle lasts from compressor ON to indoor fan OFF. For ducted units tested without an indoor fan installed, the ON cycle lasts from compressor ON to compressor OFF. For non-ducted units, the ON cycle lasts from indoor fan ON to indoor fan OFF. When testing air conditioners and heat pumps having a variable-speed compressor, avoid using an induction watt/watt-hour meter.

b. When performing section 3.5 and/or 3.8 cyclic tests on non-ducted units, provide instrumentation to determine the average electrical power consumption of the indoor fan motor to within ±1.0 percent. If required according to sections 3.3, 3.4, 3.7, 3.9.1, and/or 3.10, this same instrumentation requirement applies when testing air conditioners and heat pumps having a variable-speed constant-air-volume-rate indoor fan or a variable-speed, variable-air-volume-rate indoor fan.

2.9  Time measurements. Make elapsed time measurements using an instrument that yields readings accurate to within ±0.2 percent.

2.10  Test apparatus for the secondary space conditioning capacity measurement. For all tests, use the Indoor Air Enthalpy Method to measure the unit's capacity. This method uses the test set-up specified in sections 2.4 to 2.6. In addition, for all steady-state tests, conduct a second, independent measurement of capacity as described in section 3.1.1. For split systems, use one of the following secondary measurement methods: Outdoor Air Enthalpy Method, Compressor Calibration Method, or Refrigerant Enthalpy Method. For single packaged units, use either the Outdoor Air Enthalpy Method or the Compressor Calibration Method as the secondary measurement.

2.10.1  Outdoor Air Enthalpy Method. a. To make a secondary measurement of indoor space conditioning capacity using the Outdoor Air Enthalpy Method, do the following:

(1) Measure the electrical power consumption of the test unit;

(2) Measure the air-side capacity at the outdoor coil; and

(3) Apply a heat balance on the refrigerant cycle.

b. The test apparatus required for the Outdoor Air Enthalpy Method is a subset of the apparatus used for the Indoor Air Enthalpy Method. Required apparatus includes the following:

(1) An outlet plenum containing static pressure taps (sections 2.4, 2.4.1, and 2.5.3),

(2) An airflow measuring apparatus (section 2.6),

(3) A duct section that connects these two components and itself contains the instrumentation for measuring the dry-bulb temperature and water vapor content of the air leaving the outdoor coil (sections 2.5.4, 2.5.5, and 2.5.6), and

(4) On the inlet side, a sampling device and optional temperature grid (sections 2.5 and 2.5.2).

c. During the preliminary tests described in sections 3.11.1 and 3.11.1.1, measure the evaporator and condenser temperatures or pressures. On both the outdoor coil and the indoor coil, solder a thermocouple onto a return bend located at or near the midpoint of each coil or at points not affected by vapor superheat or liquid subcooling. Alternatively, if the test unit is not sensitive to the refrigerant charge, connect pressure gages to the access valves or to ports created from tapping into the suction and discharge lines. Use this alternative approach when testing a unit charged with a zeotropic refrigerant having a temperature glide in excess of 1°F at the specified test conditions.

2.10.2  Compressor Calibration Method. Measure refrigerant pressures and temperatures to determine the evaporator superheat and the enthalpy of the refrigerant that enters and exits the indoor coil. Determine refrigerant flow rate or, when the superheat of the refrigerant leaving the evaporator is less than 5 °F, total capacity from separate calibration tests conducted under identical operating conditions. When using this method, install instrumentation, measure refrigerant properties, and adjust the refrigerant charge according to section 7.4.2 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). Use refrigerant temperature and pressure measuring instruments that meet the specifications given in sections 5.1.1 and 5.2 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22).

2.10.3  Refrigerant Enthalpy Method. For this method, calculate space conditioning capacity by determining the refrigerant enthalpy change for the indoor coil and directly measuring the refrigerant flow rate. Use section 7.6.2 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) for the requirements for this method, including the additional instrumentation requirements, and information on placing the flow meter and a sight glass. Use refrigerant temperature, pressure, and flow measuring instruments that meet the specifications given in sections 5.1.1, 5.2, and 5.5.1 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22).

2.11  Measurement of test room ambient conditions. a. If using a test set-up where air is ducted directly from the conditioning apparatus to the indoor coil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ASHRAE Standard 37–88 (incorporated by reference, see §430.22)), add instrumentation to permit measurement of the indoor test room dry-bulb temperature.

b. If the Outdoor Air Enthalpy Method is not used, add instrumentation to measure the dry-bulb temperature and the water vapor content of the air entering the outdoor coil. If an air sampling device is used, construct and apply the device as per section 6 of ASHRAE Standard 41.1–86 (RA 01) (incorporated by reference, see §430.22). Take steps (e.g., add or re-position a lab circulating fan), as needed, to minimize the magnitude of the temperature distribution non-uniformity. Position any fan in the outdoor test room while trying to keep air velocities in the vicinity of the test unit below 500 feet per minute.

c. Measure dry bulb temperatures as specified in sections 4, 5, 6.1–6.10, 9, 10, and 11 of ASHRAE Standard 41.1–86 (RA 01) (incorporated by reference, see §430.22). Measure water vapor content as stated above in section 2.5.6.

2.12  Measurement of indoor fan speed. When required, measure fan speed using a revolution counter, tachometer, or stroboscope that gives readings accurate to within ±1.0 percent.

2.13  Measurement of barometric pressure. Determine the average barometric pressure during each test. Use an instrument that meets the requirements specified in section 5.2 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22).

3. Testing Procedures

3.1  General Requirements. If, during the testing process, an equipment set-up adjustment is made that would alter the performance of the unit when conducting an already completed test, then repeat all tests affected by the adjustment. For cyclic tests, instead of maintaining an air volume rate, for each airflow nozzle, maintain the static pressure difference or velocity pressure during an ON period at the same pressure difference or velocity pressure as measured during the steady-state test conducted at the same test conditions.

3.1.1  Primary and secondary test methods. For all tests, use the Indoor Air Enthalpy Method test apparatus to determine the unit's space conditioning capacity. The procedure and data collected, however, differ slightly depending upon whether the test is a steady-state test, a cyclic test, or a frost accumulation test. The following sections described these differences. For all steady-state tests (i.e., the A, A₂, A₁, B, B₂, B₁, C, C₁, EV, F₁, G₁, H0₁, H₁, H1₂, H1₁, HI_N, H₃, H3₂, and H3₁ Tests), in addition, use one of the acceptable secondary methods specified in section 2.10 to determine indoor space conditioning capacity. Calculate this secondary check of capacity according to section 3.11. The two capacity measurements must agree to within 6 percent to constitute a valid test. For this capacity comparison, use the Indoor Air Enthalpy Method capacity that is calculated in section 7.3 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) (and do not make the after-test fan heat adjustments described in sections 3.3, 3.4, 3.7, and 3.10 of this Appendix). However, include the appropriate section 3.3 to 3.5 and 3.7 to 3.10 fan heat adjustments within the Indoor Air Enthalpy Method capacities used for the section 4 seasonal calculations.

3.1.2  Manufacturer-provided equipment overrides. Where needed, the manufacturer must provide a means for overriding the controls of the test unit so that the compressor(s) operates at the specified speed or capacity and the indoor fan operates at the specified speed or delivers the specified air volume rate.

3.1.3  Airflow through the outdoor coil. For all tests, meet the requirements given in section 6.1.3.4 of ARI Standard 210/240–2003 (incorporated by reference, see §430.22) when obtaining the airflow through the outdoor coil.

3.1.4  Airflow through the indoor coil.

3.1.4.1  Cooling Certified Air Volume Rate.

3.1.4.1.1  Cooling Certified Air Volume Rate for Ducted Units. The manufacturer must specify the Cooling Certified Air Volume Rate. Use this value as long as the following two requirements are satisfied. First, when conducting the A or A₂ Test (exclusively), the measured air volume rate, when divided by the measured indoor air-side total cooling capacity, must not exceed 37.5 cubic feet per minute of standard air (scfm) per 1000 Btu/h. If this ratio is exceeded, reduce the air volume rate until this ratio is equaled. Use this reduced air volume rate for all tests that call for using the Cooling Certified Air Volume Rate. The second requirement is as follows:

a. For ducted units that are tested with a fixed-speed, multi-speed, or variable-speed variable-air-volume-rate indoor fan installed. For the A or A₂ Test (exclusively), the measured external static pressure must be equal to or greater than the applicable minimum external static pressure cited in Table 2. If the Table 2 minimum is not equaled or exceeded, incrementally change the set-up of the indoor fan (e.g., fan motor pin settings, fan motor speed) until the Table 2 requirement is met while maintaining the same air volume rate. If the indoor fan set-up changes cannot provide the minimum external static, then reduce the air volume rate until the correct Table 2 minimum is equaled. For the last scenario, use the reduced air volume rate for all tests that require the Cooling Certified Air Volume Rate.

b. For ducted units that are tested with a constant-air-volume-rate indoor fan installed. For all tests that specify the Cooling Certified Air Volume Rate, obtain an external static pressure as close to (but not less than) the applicable Table 2 value that does not cause instability or an automatic shutdown of the indoor blower.

c. For ducted units that are tested without an indoor fan installed. For the A or A₂ Test, (exclusively), the pressure drop across the indoor coil assembly must not exceed 0.30 inches of water. If this pressure drop is exceeded, reduce the air volume rate until the measured pressure drop equals the specified maximum. Use this reduced air volume rate for all tests that require the Cooling Certified Air Volume Rate.

3.1.4.1.2  Cooling Certified Air Volume Rate for Non-ducted Units. For non-ducted units, the Cooling Certified Air Volume Rate is the air volume rate that results during each test when the unit is operated at an external static pressure of zero inches of water.

3.1.4.2  Cooling Minimum Air Volume Rate. a. For ducted units that regulate the speed (as opposed to the cfm) of the indoor fan,

where “Cooling Minimum Fan Speed” corresponds to the fan speed used when operating at low compressor capacity (two-capacity system), the fan speed used when operating at the minimum compressor speed (variable-speed system), or the lowest fan speed used when cooling (single-speed compressor and a variable-speed variable-air-volume-rate indoor fan). For such systems, obtain the Cooling Minimum Air Volume Rate regardless of the external static pressure.

b. For ducted units that regulate the air volume rate provided by the indoor fan, the manufacturer must specify the Cooling Minimum Air Volume Rate. For such systems, conduct all tests that specify the Cooling Minimum Air Volume Rate—(i.e., the A₁, B₁, C₁, F₁, and G₁ Tests)—at an external static pressure that does not cause instability or an automatic shutdown of the indoor blower while being as close to, but not less than,

where ΔP_st,A2 is the applicable Table 2 minimum external static pressure that was targeted during the A₂ (and B₂) Test.

c. For ducted two-capacity units that are tested without an indoor fan installed, the Cooling Minimum Air Volume Rate is the higher of (1) the rate specified by the manufacturer or (2) 75 percent of the Cooling Certified Air Volume Rate. During the laboratory tests on a coil-only (fanless) unit, obtain this Cooling Minimum Air Volume Rate regardless of the pressure drop across the indoor coil assembly.

d. For non-ducted units, the Cooling Minimum Air Volume Rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water and at the indoor fan setting used at low compressor capacity (two-capacity system) or minimum compressor speed (variable-speed system). For units having a single-speed compressor and a variable-speed variable-air-volume-rate indoor fan, use the lowest fan setting allowed for cooling.

3.1.4.3  Cooling Intermediate Air Volume Rate. a. For ducted units that regulate the speed of the indoor fan,

For such units, obtain the Cooling Intermediate Air Volume Rate regardless of the external static pressure.

b. For ducted units that regulate the air volume rate provided by the indoor fan, the manufacturer must specify the Cooling Intermediate Air Volume Rate. For such systems, conduct the E_V Test at an external static pressure that does not cause instability or an automatic shutdown of the indoor blower while being as close to, but not less than,

where ΔP_st,A2 is the applicable Table 2 minimum external static pressure that was targeted during the A₂ (and B₂) Test.

c. For non-ducted units, the Cooling Intermediate Air Volume Rate is the air volume rate that results when the unit operates at an external static pressure of zero inches of water and at the fan speed selected by the controls of the unit for the E_V Test conditions.

3.1.4.4  Heating Certified Air Volume Rate.

3.1.4.4.1  Ducted heat pumps where the Heating and Cooling Certified Air Volume Rates are the same. a. Use the Cooling Certified Air Volume Rate as the Heating Certified Air Volume Rate for:

1. Ducted heat pumps that operate at the same indoor fan speed during both the A (or A₂) and the H1 (or H1₂) Tests;

2. Ducted heat pumps that regulate fan speed to deliver the same constant air volume rate during both the A (or A₂) and the H1 (or H1₂) Tests; and

3. Ducted heat pumps that are tested without an indoor fan installed (except two-capacity northern heat pumps that are tested only at low capacity cooling—see 3.1.4.4.2).

b. For heat pumps that meet the above criteria “1” and “3,” no minimum requirements apply to the measured external or internal, respectively, static pressure. For heat pumps that meet the above criterion “2,” test at an external static pressure that does not cause instability or an automatic shutdown of the indoor blower while being as close to, but not less than, the same Table 2 minimum external static pressure as was specified for the A (or A₂) cooling mode test.

3.1.4.4.2  Ducted heat pumps where the Heating and Cooling Certified Air Volume Rates are different due to indoor fan operation. a. For ducted heat pumps that regulate the speed (as opposed to the cfm) of the indoor fan,

For such heat pumps, obtain the Heating Certified Air Volume Rate without regard to the external static pressure.

b. For ducted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufacturer must specify the Heating Certified Air Volume Rate. For such heat pumps, conduct all tests that specify the Heating Certified Air Volume Rate at an external static pressure that does not cause instability or an automatic shutdown of the indoor blower while being as close to, but not less than,

where the Cooling Certified ΔP_st is the applicable Table 2 minimum external static pressure that was specified for the A or A₂ Test.

c. When testing ducted, two-capacity northern heat pumps (see Definition 1.46), use the appropriate approach of the above two cases for units that are tested with an indoor fan installed. For coil-only (fanless) northern heat pumps, the Heating Certified Air Volume Rate is the lesser of the rate specified by the manufacturer or 133 percent of the Cooling Certified Air Volume Rate. For this latter case, obtain the Heating Certified Air Volume Rate regardless of the pressure drop across the indoor coil assembly.

3.1.4.4.3  Ducted heating-only heat pumps. The manufacturer must specify the Heating Certified Air Volume Rate. Use this value when the following two requirements are satisfied. First, when conducting the H1 or H1₂ Test (exclusively), the measured air volume rate, when divided by the measured indoor air-side total heating capacity, must not exceed 37.5 cubic feet per minute of standard air (scfm) per 1000 Btu/h. If this ratio is exceeded, reduce the air volume rate until this ratio is equaled. Use this reduced air volume rate for all tests of heating-only heat pumps that call for the Heating Certified Air Volume Rate. The second requirement is as follows:

a. For heating-only heat pumps that are tested with a fixed-speed, multi-speed, or variable-speed variable-air-volume-rate indoor fan installed. For the H1 or H1₂ Test (exclusively), the measured external static pressure must be equal to or greater than the Table 2 minimum external static pressure that applies given the heating-only heat pump's rated heating capacity. If the Table 2 minimum is not equaled or exceeded, incrementally change the set-up of the indoor fan until the Table 2 requirement is met while maintaining the same air volume rate. If the indoor fan set-up changes cannot provide the necessary external static pressure, then reduce the air volume rate until the correct Table 2 minimum is equaled. For the last scenario, use the reduced air volume rate for all tests that require the Heating Certified Air Volume Rate.

b. For ducted heating-only heat pumps having a constant-air-volume-rate indoor fan. For all tests that specify the Heating Certified Air Volume Rate, obtain an external static pressure that does not cause instability or an automatic shutdown of the indoor blower while being as close to, but not less than, the applicable Table 2 minimum.

c. For ducted heating-only heat pumps that are tested without an indoor fan installed. For the H1 or H1₂ Test, (exclusively), the pressure drop across the indoor coil assembly must not exceed 0.30 inches of water. If this pressure drop is exceeded, reduce the air volume rate until the measured pressure drop equals the specified maximum. Use this reduced air volume rate for all tests that require the Heating Certified Air Volume Rate.

3.1.4.4.4  Non-ducted heat pumps, including non-ducted heating-only heat pumps. For non-ducted heat pumps, the Heating Certified Air Volume Rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water.

3.1.4.5  Heating Minimum Air Volume Rate. a. For ducted heat pumps that regulate the speed (as opposed to the cfm) of the indoor fan,

where “Heating Minimum Fan Speed” corresponds to the fan speed used when operating at low compressor capacity (two-capacity system), the lowest fan speed used at any time when operating at the minimum compressor speed (variable-speed system), or the lowest fan speed used when heating (single-speed compressor and a variable-speed variable-air-volume-rate indoor fan). For such heat pumps, obtain the Heating Minimum Air Volume Rate without regard to the external static pressure.

b. For ducted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufacturer must specify the Heating Minimum Air Volume Rate. For such heat pumps, conduct all tests that specify the Heating Minimum Air Volume Rate—(i.e., the H0₁, H1₁, H2₁, and H3₁ Tests)—at an external static pressure that does not cause instability or an automatic shutdown of the indoor blower while being as close to, but not less than,

is the minimum external static pressure that was targeted during the H1₂ Test.

c. For ducted two-capacity northern heat pumps that are tested with an indoor fan installed, use the appropriate approach of the above two cases.

d. For ducted two-capacity heat pumps that are tested without an indoor fan installed, use the Cooling Minimum Air Volume Rate as the Heating Minimum Air Volume Rate. For ducted two-capacity northern heat pumps that are tested without an indoor fan installed, use the Cooling Certified Air Volume Rate as the Heating Minimum Air Volume Rate. For ducted two-capacity heating-only heat pumps that are tested without an indoor fan installed, the Heating Minimum Air Volume Rate is the higher of the rate specified by the manufacturer or 75 percent of the Heating Certified Air Volume Rate. During the laboratory tests on a coil-only (fanless) unit, obtain the Heating Minimum Air Volume Rate without regard to the pressure drop across the indoor coil assembly.

e. For non-ducted heat pumps, the Heating Minimum Air Volume Rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water and at the indoor fan setting used at low compressor capacity (two-capacity system) or minimum compressor speed (variable-speed system). For units having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor fan, use the lowest fan setting allowed for heating.

3.1.4.6  Heating Intermediate Air Volume Rate. a. For ducted heat pumps that regulate the speed of the indoor fan,

For such heat pumps, obtain the Heating Intermediate Air Volume Rate without regard to the external static pressure.

b. For ducted heat pumps that regulate the air volume rate delivered by the indoor fan, the manufacturer must specify the Heating Intermediate Air Volume Rate. For such heat pumps, conduct the H2_V Test at an external static pressure that does not cause instability or an automatic shutdown of the indoor blower while being as close to, but not less than,

is the minimum external static pressure that was specified for the H1₂ Test.

c. For non-ducted heat pumps, the Heating Intermediate Air Volume Rate is the air volume rate that results when the heat pump operates at an external static pressure of zero inches of water and at the fan speed selected by the controls of the unit for the H2_V Test conditions.

3.1.4.7  Heating Nominal Air Volume Rate. Except for the noted changes, determine the Heating Nominal Air Volume Rate using the approach described in section 3.1.4.6. Required changes include substituting “H1_N Test” for H2_V Test” within the first section 3.1.4.6 equation, substituting “H1_N Test ΔP_st” for “H2_V Test ΔP_st” in the second section 3.1.4.6 equation, substituting “H1_N Test” for each “H2_V Test”, and substituting “Heating Nominal Air Volume Rate” for each “Heating Intermediate Air Volume Rate.”

3.1.5  Indoor test room requirement when the air surrounding the indoor unit is not supplied from the same source as the air entering the indoor unit. If using a test set-up where air is ducted directly from the air reconditioning apparatus to the indoor coil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ASHRAE Standard 37–88) (incorporated by reference, see §430.22), maintain the dry bulb temperature within the test room within ±5.0 °F of the applicable sections 3.2 and 3.6 dry bulb temperature test condition for the air entering the indoor unit.

3.1.6  Air volume rate calculations. For all steady-state tests and for frost accumulation (H2, H2₁, H2₂, H2_V) tests, calculate the air volume rate through the indoor coil as specified in sections 7.8.3.1 and 7.8.3.2 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). When using the Outdoor Air Enthalpy Method, follow sections 7.8.3.1 and 7.8.3.2 to calculate the air volume rate through the outdoor coil. To express air volume rates in terms of standard air, use:

where,

V _s = air volume rate of standard (dry) air, (ft³ /min)_da

V _mx = air volume rate of the air-water vapor mixture, (ft³ /min)_mx

v_n' = specific volume of air-water vapor mixture at the nozzle, ft³ per lbm of the air-water vapor mixture

W_n = humidity ratio at the nozzle, lbm of water vapor per lbm of dry air

0.075 = the density associated with standard (dry) air, (lbm/ft³ )

v_n = specific volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor content, and barometric pressure existing at the nozzle, ft³ per lbm of dry air.

3.1.7  Test sequence. When testing a ducted unit (except if a heating-only heat pump), conduct the A or A₂ Test first to establish the Cooling Certified Air Volume Rate. For ducted heat pumps where the Heating and Cooling Certified Air Volume Rates are different, make the first heating mode test one that requires the Heating Certified Air Volume Rate. For ducted heating-only heat pumps, conduct the H1 or H1₂ Test first to establish the Heating Certified Air Volume Rate. When conducting an optional cyclic test, always conduct it immediately after the steady-state test that requires the same test conditions. For variable-speed systems, the first test using the Cooling Minimum Air Volume Rate should precede the E_V Test if one expects to adjust the indoor fan control options when preparing for the first Minimum Air Volume Rate test. Under the same circumstances, the first test using the Heating Minimum Air Volume Rate should precede the H2_V Test. The test laboratory makes all other decisions on the test sequence.

3.1.8  Requirement for the air temperature distribution leaving the indoor coil. For at least the first cooling mode test and the first heating mode test, monitor the temperature distribution of the air leaving the indoor coil using the grid of individual sensors described in sections 2.5 and 2.5.4. For the 30-minute data collection interval used to determine capacity, the maximum spread among the outlet dry bulb temperatures from any data sampling must not exceed 1.5 °F. Install the mixing devices described in section 2.5.4.2 to minimize the temperature spread.

3.1.9  Control of auxiliary resistive heating elements. Except as noted, disable heat pump resistance elements used for heating indoor air at all times, including during defrost cycles and if they are normally regulated by a heat comfort controller. For heat pumps equipped with a heat comfort controller, enable the heat pump resistance elements only during the below-described, short test. For single-speed heat pumps covered under section 3.6.1, the short test follows the H1 or, if conducted, the H1C Test. For two-capacity heat pumps and heat pumps covered under section 3.6.2, the short test follows the H1₂ Test. Set the heat comfort controller to provide the maximum supply air temperature. With the heat pump operating and while maintaining the Heating Certified Air Volume Rate, measure the temperature of the air leaving the indoor-side beginning 5 minutes after activating the heat comfort controller. Sample the outlet dry-bulb temperature at regular intervals that span 5 minutes or less. Collect data for 10 minutes, obtaining at least 3 samples. Calculate the average outlet temperature over the 10-minute interval, T_CC.

3.2  Cooling mode tests for different types of air conditioners and heat pumps.

3.2.1  Tests for a unit having a single-speed compressor that is tested with a fixed-speed indoor fan installed, with a constant-air-volume-rate indoor fan installed, or with no indoor fan installed. Conduct two steady-state wet coil tests, the A and B Tests. Use the two optional dry-coil tests, the steady-state C Test and the cyclic D Test, to determine the cooling mode cyclic degradation coefficient, C_D^c. If the two optional tests are not conducted, assign C_D^c the default value of 0.25. Table 3 specifies test conditions for these four tests.

3.2.2  Tests for a unit having a single-speed compressor and a variable-speed variable-air-volume-rate indoor fan installed.

3.2.2.1  Indoor fan capacity modulation that correlates with the outdoor dry bulb temperature. Conduct four steady-state wet coil tests: The A₂, A₁ , B₂, and B₁ Tests. Use the two optional dry-coil tests, the steady-state C₁ Test and the cyclic D₁ Test, to determine the cooling mode cyclic degradation coefficient, C_D^c. If the two optional tests are not conducted, assign C_D^c the default value of 0.25. Table 4 specifies test conditions for these six tests.

3.2.2.2  Indoor fan capacity modulation based on adjusting the sensible to total (S/T) cooling capacity ratio. The testing requirements are the same as specified in section 3.2.1 and Table 3. Use a Cooling Certified Air Volume Rate that represents a normal residential installation. If performed, conduct the steady-state C Test and the cyclic D Test with the unit operating in the same S/T capacity control mode as used for the B Test.

3.2.3  Tests for a unit having a two-capacity compressor. (See Definition 1.45.) a. Conduct four steady-state wet coil tests: The A₂, A₁, B₂, and B₁ Tests. Use the two optional dry-coil tests, the steady-state C₁ Test and the cyclic D₁ Test, to determine the cooling mode cyclic degradation coefficient, C_D^c. If the two optional tests are not conducted, assign C_D^c the default value of 0.25. Table 5 specifies test conditions for these six tests.

b. For units having a variable speed indoor fan that is modulated to adjust the sensible to total (S/T) cooling capacity ratio, use Cooling Certified and Cooling Minimum Air Volume Rates that represent a normal residential installation. Additionally, if conducting the optional dry-coil tests, operate the unit in the same S/T capacity control mode as used for the B₁ Test.

c. Test two-capacity, northern heat pumps (see Definition 1.46) in the same way as a single speed heat pump with the unit operating exclusively at low compressor capacity (see section 3.2.1 and Table 3).

d. If a two-capacity air conditioner or heat pump locks out low capacity operation at outdoor temperatures that are less than 95 °F, conduct the A₁ Test using the outdoor temperature conditions listed for the F₁ Test in Table 6 rather than using the outdoor temperature conditions listed in Table 5 for the A₁ Test.

3.2.4  Tests for a unit having a variable-speed compressor. a. Conduct five steady-state wet coil tests: The A₂, E_V, B₂, B₁, and F₁ Tests. Use the two optional dry-coil tests, the steady-state G₁ Test and the cyclic I₁ Test, to determine the cooling mode cyclic degradation coefficient,C_D^c. If the two optional tests are not conducted, assign C_D^c the default value of 0.25. Table 6 specifies test conditions for these seven tests. Determine the intermediate compressor speed cited in Table 6 using:

where a tolerance of plus 5 percent or the next higher inverter frequency step from that calculated is allowed.

b. For units that modulate the indoor fan speed to adjust the sensible to total (S/T) cooling capacity ratio, use Cooling Certified, Cooling Intermediate, and Cooling Minimum Air Volume Rates that represent a normal residential installation. Additionally, if conducting the optional dry-coil tests, operate the unit in the same S/T capacity control mode as used for the F₁ Test.

3.3  Test procedures for steady-state wet coil cooling mode tests (the A, A₂, A₁, B, B₂, B₁, E_V, and F₁ Tests). a. For the pretest interval, operate the test room reconditioning apparatus and the unit to be tested until maintaining equilibrium conditions for at least 30 minutes at the specified section 3.2 test conditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor fan of the test unit to obtain and then maintain the indoor air volume rate and/or external static pressure specified for the particular test. Continuously record (see Definition 1.15):

(1) The dry-bulb temperature of the air entering the indoor coil,

(2) The water vapor content of the air entering the indoor coil,

(3) The dry-bulb temperature of the air entering the outdoor coil, and

(4) For the section 2.2.4 cases where its control is required, the water vapor content of the air entering the outdoor coil.

Refer to section 3.11 for additional requirements that depend on the selected secondary test method.

b. After satisfying the pretest equilibrium requirements, make the measurements specified in Table 5 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) for the Indoor Air Enthalpy method and the user-selected secondary method. Except for external static pressure, make the Table 5 measurements at equal intervals that span 10 minutes or less. Measure external static pressure every 5 minutes or less. Continue data sampling until reaching a 30-minute period (e.g., four consecutive 10-minute samples) where the test tolerances specified in Table 7 are satisfied. For those continuously recorded parameters, use the entire data set from the 30-minute interval to evaluate Table 7 compliance. Determine the average electrical power consumption of the air conditioner or heat pump over the same 30-minute interval.

c. Calculate indoor-side total cooling capacity as specified in section 7.3.3.1 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). Do not adjust the parameters used in calculating capacity for the permitted variations in test conditions. Evaluate air enthalpies based on the measured barometric pressure. Assign the average total space cooling capacity and electrical power consumption over the 30-minute data collection interval to the variables Q _c^k(T) and E _c^k(T), respectively. For these two variables, replace the “T” with the nominal outdoor temperature at which the test was conducted. The superscript k is used only when testing multi-capacity units. Use the superscript k=2 to denote a test with the unit operating at high capacity or maximum speed, k=1 to denote low capacity or minimum speed, and k=v to denote the intermediate speed.

d. For units tested without an indoor fan installed, decrease Q _c^k(T) by

and increase E _c^k(T) by,

where V _s is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

d. For air conditioners and heat pumps having a constant-air-volume-rate indoor fan, the five additional steps listed below are required if the average of the measured external static pressures exceeds the applicable sections 3.1.4 minimum (or target) external static pressure (ΔP_min) by 0.03 inches of water or more.

1. Measure the average power consumption of the indoor fan motor (E _fan,1) and record the corresponding external static pressure (ΔP₁) during or immediately following the 30-minute interval used for determining capacity.

2. After completing the 30-minute interval and while maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP₁ + (ΔP₁ − ΔP_min).

3. After re-establishing steady readings of the fan motor power and external static pressure, determine average values for the indoor fan power (E _fan,2) and the external static pressure (ΔP₂) by making measurements over a 5-minute interval.

4. Approximate the average power consumption of the indoor fan motor at ΔP_min using linear extrapolation:

5. Increase the total space cooling capacity, Q _c^k(T), by the quantity (E _fan,1 − E _fan,min), when expressed on a Btu/h basis. Decrease the total electrical power, E _c^k(T), by the same fan power difference, now expressed in watts.

3.4  Test procedures for the optional steady-state dry coil cooling mode tests (the C, C₁, and G₁ Tests). a. Except for the modifications noted in this section, conduct the steady-state dry coil cooling mode tests as specified in section 3.3 for wet coil tests. Prior to recording data during the steady-state dry coil test, operate the unit at least one hour after achieving dry coil conditions. Drain the drain pan and plug the drain opening. Thereafter, the drain pan should remain completely dry.

b. Denote the resulting total space cooling capacity and electrical power derived from the test as Q _ss,dry and E _ss,dry(T). In preparing for the section 3.5 cyclic test, record the average indoor-side air volume rate, V , specific heat of the air, C_p,a (expressed on dry air basis), specific volume of the air at the nozzles, v'_n, humidity ratio at the nozzles, W_n, and either pressure difference or velocity pressure for the flow nozzles. For units having a variable-speed indoor fan (that provides either a constant or variable air volume rate) that will or may be tested during the cyclic dry coil cooling mode test with the indoor fan turned off (see section 3.5), include the electrical power used by the indoor fan motor among the recorded parameters from the 30-minute test.

3.5  Test procedures for the optional cyclic dry coil cooling mode tests (the D, D₁, and I₁ Tests). a. After completing the steady-state dry-coil test, remove the Outdoor Air Enthalpy method test apparatus, if connected, and begin manual OFF/ON cycling of the unit's compressor. The test set-up should otherwise be identical to the set-up used during the steady-state dry coil test. When testing heat pumps, leave the reversing valve during the compressor OFF cycles in the same position as used for the compressor ON cycles, unless automatically changed by the controls of the unit. For units having a variable-speed indoor fan, the manufacturer has the option of electing at the outset whether to conduct the cyclic test with the indoor fan enabled or disabled. Always revert to testing with the indoor fan disabled if cyclic testing with the fan enabled is unsuccessful.

b. For units having a single-speed or two-capacity compressor, cycle the compressor OFF for 24 minutes and then ON for 6 minutes (Δτ_cyc,dry = 0.5 hours). For units having a variable-speed compressor, cycle the compressor OFF for 48 minutes and then ON for 12 minutes (Δτ_cyc,dry = 1.0 hours). Repeat the OFF/ON compressor cycling pattern until the test is completed. Allow the controls of the unit to regulate cycling of the outdoor fan.

c. Sections 3.5.1 and 3.5.2 specify airflow requirements through the indoor coil of ducted and non-ducted systems, respectively. In all cases, use the exhaust fan of the airflow measuring apparatus (covered under section 2.6) along with the indoor fan of the unit, if installed and operating, to approximate a step response in the indoor coil airflow. Regulate the exhaust fan to quickly obtain and then maintain the flow nozzle static pressure difference or velocity pressure at the same value as was measured during the steady-state dry coil test. The pressure difference or velocity pressure should be within 2 percent of the value from the steady-state dry coil test within 15 seconds after airflow initiation. For units having a variable-speed indoor fan that ramps when cycling on and/or off, use the exhaust fan of the airflow measuring apparatus to impose a step response that begins at the initiation of ramp up and ends at the termination of ramp down.

d. For units having a variable-speed indoor fan, conduct the cyclic dry coil test using the pull-thru approach described below if any of the following occur when testing with the fan operating:

(1) The test unit automatically cycles off;

(2) Its blower motor reverses; or

(3) The unit operates for more than 30 seconds at an external static pressure that is 0.1 inches of water or more higher than the value measured during the prior steady-state test.

For the pull-thru approach, disable the indoor fan and use the exhaust fan of the airflow measuring apparatus to generate the specified flow nozzles static pressure difference or velocity pressure. If the exhaust fan cannot deliver the required pressure difference because of resistance created by the unpowered blower, temporarily remove the blower.

e. After completing a minimum of two complete compressor OFF/ON cycles, determine the overall cooling delivered and total electrical energy consumption during any subsequent data collection interval where the test tolerances given in Table 8 are satisfied. If available, use electric resistance heaters (see section 2.1) to minimize the variation in the inlet air temperature.

f. With regard to the Table 8 parameters, continuously record the dry-bulb temperature of the air entering the indoor and outdoor coils during periods when air flows through the respective coils. Sample the water vapor content of the indoor coil inlet air at least every 2 minutes during periods when air flows through the coil. Record external static pressure and the air volume rate indicator (either nozzle pressure difference or velocity pressure) at least every minute during the interval that air flows through the indoor coil. (These regular measurements of the airflow rate indicator are in addition to the required measurement at 15 seconds after flow initiation.) Sample the electrical voltage at least every 2 minutes beginning 30 seconds after compressor start-up. Continue until the compressor, the outdoor fan, and the indoor fan (if it is installed and operating) cycle off.

g. For ducted units, continuously record the dry-bulb temperature of the air entering (as noted above) and leaving the indoor coil. Or if using a thermopile, continuously record the difference between these two temperatures during the interval that air flows through the indoor coil. For non-ducted units, make the same dry-bulb temperature measurements beginning when the compressor cycles on and ending when indoor coil airflow ceases.

h. Integrate the electrical power over complete cycles of length Δτ_cyc,dry. For ducted units tested with an indoor fan installed and operating, integrate electrical power from indoor fan OFF to indoor fan OFF. For all other ducted units and for non-ducted units, integrate electrical power from compressor OFF to compressor OFF. (Some cyclic tests will use the same data collection intervals to determine the electrical energy and the total space cooling. For other units, terminate data collection used to determine the electrical energy before terminating data collection used to determine total space cooling.)

i. If the Table 8 tolerances are satisfied over the complete cycle, record the measured electrical energy consumption as e_cyc,dry and express it in units of watt-hours. Calculate the total space cooling delivered, q_cyc,dry, in units of Btu using,

where V , C_p,a, v_n' (or v_n), and W_n are the values recorded during the section 3.4 dry coil steady-state test and,

T_al(τ) = dry bulb temperature of the air entering the indoor coil at time τ, °F.

T_a2(τ) = dry bulb temperature of the air leaving the indoor coil at time τ, °F.

τ₁ = for ducted units, the elapsed time when airflow is initiated through the indoor coil; for non-ducted units, the elapsed time when the compressor is cycled on, hr.

τ₂ = the elapsed time when indoor coil airflow ceases, hr.

3.5.1  Procedures when testing ducted systems. The automatic controls that are normally installed with the test unit must govern the OFF/ON cycling of the air moving equipment on the indoor side (exhaust fan of the airflow measuring apparatus and, if installed, the indoor fan of the test unit). For example, for ducted units tested without an indoor fan installed but rated based on using a fan time delay relay, control the indoor coil airflow according to the rated ON and/or OFF delays provided by the relay. For ducted units having a variable-speed indoor fan that has been disabled (and possibly removed), start and stop the indoor airflow at the same instances as if the fan were enabled. For all other ducted units tested without an indoor fan installed, cycle the indoor coil airflow in unison with the cycling of the compressor. Close air dampers on the inlet (section 2.5.1) and outlet side (sections 2.5 and 2.5.4) during the OFF period. Airflow through the indoor coil should stop within 3 seconds after the automatic controls of the test unit (act to) de-energize the indoor fan. For ducted units tested without an indoor fan installed (excluding the special case where a variable-speed fan is temporarily removed), increase e_cyc,dry by the quantity,

and decrease q_cyc,dry by,

where V _s is the average indoor air volume rate from the section 3.4 dry coil steady-state test and is expressed in units of cubic feet per minute of standard air (scfm). For units having a variable-speed indoor fan that is disabled during the cyclic test, increase e_cyc,dry and decrease q_cyc,dry based on:

a. The product of [τ_{2 − τ1}] and the indoor fan power measured during or following the dry coil steady-state test; or,

b. The following algorithm if the indoor fan ramps its speed when cycling.

1. Measure the electrical power consumed by the variable-speed indoor fan at a minimum of three operating conditions: at the speed/air volume rate/external static pressure that was measured during the steady-state test, at operating conditions associated with the midpoint of the ramp-up interval, and at conditions associated with the midpoint of the ramp-down interval. For these measurements, the tolerances on the airflow volume or the external static pressure are the same as required for the section 3.4 steady-state test.

2. For each case, determine the fan power from measurements made over a minimum of 5 minutes.

3. Approximate the electrical energy consumption of the indoor fan if it had operated during the cyclic test using all three power measurements. Assume a linear profile during the ramp intervals. The manufacturer must provide the durations of the ramp-up and ramp-down intervals. If a manufacturer-supplied ramp interval exceeds 45 seconds, use a 45-second ramp interval nonetheless when estimating the fan energy.

The manufacturer is allowed to choose option a, and forego the extra testing burden of option b, even if the unit ramps indoor fan speed when cycling.

3.5.2  Procedures when testing non-ducted systems. Do not use air dampers when conducting cyclic tests on non-ducted units. Until the last OFF/ON compressor cycle, airflow through the indoor coil must cycle off and on in unison with the compressor. For the last OFF/ON compressor cycle—the one used to determine e_cyc,dry and q_cyc,dry—use the exhaust fan of the airflow measuring apparatus and the indoor fan of the test unit to have indoor airflow start 3 minutes prior to compressor cut-on and end three minutes after compressor cutoff. Subtract the electrical energy used by the indoor fan during the 3 minutes prior to compressor cut-on from the integrated electrical energy, e_cyc,dry. Add the electrical energy used by the indoor fan during the 3 minutes after compressor cutoff to the integrated cooling capacity, q_cyc,dry. For the case where the non-ducted unit uses a variable-speed indoor fan which is disabled during the cyclic test, correct e_cyc,dry and q_cyc,dry using the same approach as prescribed in section 3.5.1 for ducted units having a disabled variable-speed indoor fan.

3.5.3  Cooling mode cyclic degradation coefficient calculation. Use two optional dry-coil tests to determine the cooling mode cyclic degradation coefficient, C_D^c. If the two optional tests are not conducted, assign C_D^c the default value of 0.25. Evaluate C_D^c using the above results and those from the section 3.4 dry coil steady-state test.

where,

the average energy efficiency ratio during the cyclic dry coil cooling mode

test, Btu/W·h

the average energy efficiency ratio during the steady-state dry coil cooling mode test, Btu/W·h

the cooling load factor dimensionless.

Round the calculated value for C_D^c to the nearest 0.01. If C_D^c is negative, then set it equal to zero.

3.6  Heating mode tests for different types of heat pumps, including heating-only heat pumps.

3.6.1  Tests for a heat pump having a single-speed compressor that is tested with a fixed speed indoor fan installed, with a constant-air-volume-rate indoor fan installed, or with no indoor fan installed. Conduct three tests: The High Temperature (H1) Test, the Frost Accumulation (H2) Test, and the Low Temperature (H3) Test. Conduct the optional High Temperature Cyclic (H1C) Test to determine the heating mode cyclic degradation coefficient, C_D^h. If this optional test is not conducted, assign C_D^h the default value of 0.25. Test conditions for these four tests are specified in Table 9.

3.6.2  Tests for a heat pump having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor fan: capacity modulation correlates with outdoor dry bulb temperature. Conduct five tests: two High Temperature Tests (H1₂ and H1₁), one Frost Accumulation Test (H2₂), and two Low Temperature Tests (H3₂ and H3₁). Conducting an additional Frost Accumulation Test (H2₁) is optional. Conduct the optional High Temperature Cyclic (H1C₁) Test to determine the heating mode cyclic degradation coefficient, C_D^h. If this optional test is not conducted, assign C_D^h the default value of 0.25. Table 10 specifies test conditions for these seven tests. If the optional H2₁ Test is not done, use the following equations to approximate the capacity and electrical power of the heat pump at the H2₁ test conditions:

where,

The quantities Q _hk=2(47), E _hk=2(47), Q _hk=1(47), and E _hk=1(47) are determined from the H1₂ and H1₁ Tests and evaluated as specified in section 3.7; the quantities Q _hk=2(35) and E _hk=2(35) are determined from the H2₂ Test and evaluated as specified in section 3.9; and the quantities Q _hk=2(17), E _hk=2(17), Q _hk=1(17), and E _hk=1(17), are determined from the H3₂ and H3₁ Tests and evaluated as specified in section 3.10.

3.6.3  Tests for a heat pump having a two-capacity compressor (see Definition 1.45), including two-capacity, northern heat pumps (see Definition 1.46). a. Conduct one Maximum Temperature Test (H0₁), two High Temperature Tests (H1₂ and H1₁), one Frost Accumulation Test (H2₂), and one Low Temperature Test (H3₂). Conduct an additional Frost Accumulation Test (H2₁) and Low Temperature Test (H3₁) if both of the following conditions exist:

1. Knowledge of the heat pump's capacity and electrical power at low compressor capacity for outdoor temperatures of 37 °F and less is needed to complete the section 4.2.3 seasonal performance calculations, and

2. The heat pump's controls allow low capacity operation at outdoor temperatures of 37 °F and less.

b. Conduct the optional Maximum Temperature Cyclic Test (H0C₁) to determine the heating mode cyclic degradation coefficient, C_D^h. If this optional test is not conducted, assign C_D^h the default value of 0.25. Table 11 specifies test conditions for these eight tests.

3.6.4  Tests for a heat pump having a variable-speed compressor. a. Conduct one Maximum Temperature Test (H0₁), two High Temperature Tests (H1₂ and H1₁), one Frost Accumulation Test (H2_V), and one Low Temperature Test (H3₂). Conducting one or both of the following tests is optional: An additional High Temperature Test (H1_N ) and an additional Frost Accumulation Test (H2₂). Conduct the optional Maximum Temperature Cyclic (H0C₁) Test to determine the heating mode cyclic degradation coefficient, C_D^h. If this optional test is not conducted, assign C_D^h the default value of 0.25. Table 12 specifies test conditions for these eight tests. Determine the intermediate compressor speed cited in Table 12 using the heating mode maximum and minimum compressors speeds and:

where a tolerance of plus 5 percent or the next higher inverter frequency step from that calculated is allowed. If the H2₂ Test is not done, use the following equations to approximate the capacity and electrical power at the H2₂ test conditions:

b. Determine the quantities Q _hk=2(47) and from E _hk=2(47) from the H1₂ Test and evaluate them according to section 3.7. Determine the quantities Q _hk=2(17) and E _hk=2(17) from the H3₂ Test and evaluate them according to section 3.10. For heat pumps where the heating mode maximum compressor speed exceeds its cooling mode maximum compressor speed, conduct the H1_N Test if the manufacturer requests it. If the H1_N Test is done, operate the heat pump's compressor at the same speed as the speed used for the cooling mode A₂ Test. Refer to the last sentence of section 4.2 to see how the results of the H1_N Test may be used in calculating the heating seasonal performance factor.

3.6.5  Additional test for a heat pump having a heat comfort controller. Test any heat pump that has a heat comfort controller (see Definition 1.28) according to section 3.6.1, 3.6.2, or 3.6.3, whichever applies, with the heat comfort controller disabled. Additionally, conduct the abbreviated test described in section 3.1.9 with the heat comfort controller active to determine the system's maximum supply air temperature. (Note: heat pumps having a variable speed compressor and a heat comfort controller are not covered in the test procedure at this time.)

3.7  Test procedures for steady-state Maximum Temperature and High Temperature heating mode tests (the H0₁, H1, H1₂, H1₁, and H1_N Tests). a. For the pretest interval, operate the test room reconditioning apparatus and the heat pump until equilibrium conditions are maintained for at least 30 minutes at the specified section 3.6 test conditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor fan of the heat pump to obtain and then maintain the indoor air volume rate and/or the external static pressure specified for the particular test. Continuously record the dry-bulb temperature of the air entering the indoor coil, and the dry-bulb temperature and water vapor content of the air entering the outdoor coil. Refer to section 3.11 for additional requirements that depend on the selected secondary test method. After satisfying the pretest equilibrium requirements, make the measurements specified in Table 5 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) for the Indoor Air Enthalpy method and the user-selected secondary method. Except for external static pressure, make the Table 5 measurements at equal intervals that span 10 minutes or less. Measure external static pressure every 5 minutes or less. Continue data sampling until a 30-minute period (e.g., four consecutive 10-minute samples) is reached where the test tolerances specified in Table 13 are satisfied. For those continuously recorded parameters, use the entire data set for the 30-minute interval when evaluating Table 13 compliance. Determine the average electrical power consumption of the heat pump over the same 30-minute interval.

b. Calculate indoor-side total heating capacity as specified in section 7.3.4.1 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). Do not adjust the parameters used in calculating capacity for the permitted variations in test conditions. Assign the average space heating capacity and electrical power over the 30-minute data collection interval to the variables Q _h^k and E _h^k(T) respectively. The “T” and superscripted “k” are the same as described in section 3.3. Additionally, for the heating mode, use the superscript to denote results from the optional H1_N Test, if conducted.

c. For heat pumps tested without an indoor fan installed, increase Q _h^k(T) by

and increase E _h^k(T) by,

where V _s is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm). During the 30-minute data collection interval of a High Temperature Test, pay attention to preventing a defrost cycle. Prior to this time, allow the heat pump to perform a defrost cycle if automatically initiated by its own controls. As in all cases, wait for the heat pump's defrost controls to automatically terminate the defrost cycle. Heat pumps that undergo a defrost should operate in the heating mode for at least 10 minutes after defrost termination prior to beginning the 30-minute data collection interval. For some heat pumps, frost may accumulate on the outdoor coil during a High Temperature test. If the indoor coil leaving air temperature or the difference between the leaving and entering air temperatures decreases by more than 1.5 °F over the 30-minute data collection interval, then do not use the collected data to determine capacity. Instead, initiate a defrost cycle. Begin collecting data no sooner than 10 minutes after defrost termination. Collect 30 minutes of new data during which the Table 13 test tolerances are satisfied. In this case, use only the results from the second 30-minute data collection interval to evaluate Q _h^k(47) and E _h^k(47).

d. If conducting the optional cyclic heating mode test, which is described in section 3.8, record the average indoor-side air volume rate, V , specific heat of the air, C_p,a (expressed on dry air basis), specific volume of the air at the nozzles, v_n' (or v_n), humidity ratio at the nozzles, W_n, and either pressure difference or velocity pressure for the flow nozzles. If either or both of the below criteria apply, determine the average, steady-state, electrical power consumption of the indoor fan motor (E _fan,1):

1. The section 3.8 cyclic test will be conducted and the heat pump has a variable-speed indoor fan that is expected to be disabled during the cyclic test; or

2. The heat pump has a (variable-speed) constant-air volume-rate indoor fan and during the steady-state test the average external static pressure (ΔP₁) exceeds the applicable section 3.1.4.4 minimum (or targeted) external static pressure (ΔP_min) by 0.03 inches of water or more.

Determine E _fan,1 by making measurements during the 30-minute data collection interval, or immediately following the test and prior to changing the test conditions. When the above “2” criteria applies, conduct the following four steps after determining E _fan,1 (which corresponds to ΔP₁):

i. While maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP₁ + (ΔP₁ − ΔP_min).

ii. After re-establishing steady readings for fan motor power and external static pressure, determine average values for the indoor fan power (E _fan,2) and the external static pressure (ΔP₂) by making measurements over a 5-minute interval.

iii. Approximate the average power consumption of the indoor fan motor if the 30-minute test had been conducted at ΔP_min using linear extrapolation:

iv. Decrease the total space heating capacity, Q _h^k(T), by the quantity (E _fan,1 − E _fan,min), when expressed on a Btu/h basis. Decrease the total electrical power, E _h^k(T) by the same fan power difference, now expressed in watts.

3.8 Test procedures for the optional cyclic heating mode tests (the H0C₁, H1C, and H1C₁ Tests). a. Except as noted below, conduct the cyclic heating mode test as specified in section 3.5. As adapted to the heating mode, replace section 3.5 references to “the steady-state dry coil test” with “the heating mode steady-state test conducted at the same test conditions as the cyclic heating mode test.” Use the test tolerances in Table 14 rather than Table 8. Record the outdoor coil entering wet-bulb temperature according to the requirements given in section 3.5 for the outdoor coil entering dry-bulb temperature. Drop the subscript “dry” used in variables cited in section 3.5 when referring to quantities from the cyclic heating mode test. Determine the total space heating delivered during the cyclic heating test, q_cyc, as specified in section 3.5 except for making the following changes:

(1) When evaluating Equation 3.5–1, use the values of V , C_p,a,v_n', (or v_n), and W_n that were recorded during the section 3.7 steady-state test conducted at the same test conditions.

(2) Calculate Γ using,

b. For ducted heat pumps tested without an indoor fan installed (excluding the special case where a variable-speed fan is temporarily removed), increase q_cyc by the amount calculated using Equation 3.5–3. Additionally, increase e_cyc by the amount calculated using Equation 3.5–2. In making these calculations, use the average indoor air volume rate (V _s) determined from the section 3.7 steady-state heating mode test conducted at the same test conditions.

c. For non-ducted heat pumps, subtract the electrical energy used by the indoor fan during the 3 minutes after compressor cutoff from the non-ducted heat pump's integrated heating capacity, q_cyc.

d. If a heat pump defrost cycle is manually or automatically initiated immediately prior to or during the OFF/ON cycling, operate the heat pump continuously until 10 minutes after defrost termination. After that, begin cycling the heat pump immediately or delay until the specified test conditions have been re-established. Pay attention to preventing defrosts after beginning the cycling process. For heat pumps that cycle off the indoor fan during a defrost cycle, make no effort here to restrict the air movement through the indoor coil while the fan is off. Resume the OFF/ON cycling while conducting a minimum of two complete compressor OFF/ON cycles before determining q_cyc and e_cyc.

3.8.1  Heating mode cyclic degradation coefficient calculation. Use the results from the optional cyclic test and the required steady-state test that were conducted at the same test conditions to determine the heating mode cyclic degradation coefficient, C_D^h. If the optional test is not conducted, assign C_D^h the default value of 0.25.

where,

the average coefficient of performance during the cyclic heating mode test, dimensionless.

the average coefficient of performance during the steady-state heating mode test conducted at the same test conditions—i.e., same outdoor dry bulb temperature, T_cyc, and speed/capacity, k, if applicable—as specified for the cyclic heating mode test, dimensionless.

the heating load factor, dimensionless.

T_cyc = the nominal outdoor temperature at which the cyclic heating mode test is conducted, 62 or 47 °F.

Δτ_cyc = the duration of the OFF/ON intervals; 0.5 hours when testing a heat pump having a single-speed or two-capacity compressor and 1.0 hour when testing a heat pump having a variable-speed compressor.

Round the calculated value for C_D^h to the nearest 0.01. If C_D^h is negative, then set it equal to zero.

3.9  Test procedures for Frost Accumulation heating mode tests (the H2, H2₂, H2_V, and H2₁ Tests). a. Confirm that the defrost controls of the heat pump are set as specified in section 2.2.1. Operate the test room reconditioning apparatus and the heat pump for at least 30 minutes at the specified section 3.6 test conditions before starting the “preliminary” test period. The preliminary test period must immediately precede the “official” test period, which is the heating and defrost interval over which data are collected for evaluating average space heating capacity and average electrical power consumption.

b. For heat pumps containing defrost controls which are likely to cause defrosts at intervals less than one hour, the preliminary test period starts at the termination of an automatic defrost cycle and ends at the termination of the next occurring automatic defrost cycle. For heat pumps containing defrost controls which are likely to cause defrosts at intervals exceeding one hour, the preliminary test period must consist of a heating interval lasting at least one hour followed by a defrost cycle that is either manually or automatically initiated. In all cases, the heat pump's own controls must govern when a defrost cycle terminates.

c. The official test period begins when the preliminary test period ends, at defrost termination. The official test period ends at the termination of the next occurring automatic defrost cycle. When testing a heat pump that uses a time-adaptive defrost control system (see Definition 1.42), however, manually initiate the defrost cycle that ends the official test period at the instant indicated by instructions provided by the manufacturer. If the heat pump has not undergone a defrost after 12 hours, immediately conclude the test and use the results from the full 12-hour period to calculate the average space heating capacity and average electrical power consumption. For heat pumps that turn the indoor fan off during the defrost cycle, take steps to cease forced airflow through the indoor coil and block the outlet duct whenever the heat pump's controls cycle off the indoor fan. If it is installed, use the outlet damper box described in section 2.5.4.1 to affect the blocked outlet duct.

d. Defrost termination occurs when the controls of the heat pump actuate the first change in converting from defrost operation to normal heating operation. Defrost initiation occurs when the controls of the heat pump first alter its normal heating operation in order to eliminate possible accumulations of frost on the outdoor coil.

e. To constitute a valid Frost Accumulation test, satisfy the test tolerances specified in Table 15 during both the preliminary and official test periods. As noted in Table 15, test operating tolerances are specified for two sub-intervals: (1) When heating, except for the first 10 minutes after the termination of a defrost cycle (Sub-interval H, as described in Table 15) and (2) when defrosting, plus these same first 10 minutes after defrost termination (Sub-interval D, as described in Table 15). Evaluate compliance with Table 15 test condition tolerances and the majority of the test operating tolerances using the averages from measurements recorded only during Sub-interval H. Continuously record the dry bulb temperature of the air entering the indoor coil, and the dry bulb temperature and water vapor content of the air entering the outdoor coil. Sample the remaining parameters listed in Table 15 at equal intervals that span 10 minutes or less.

f. For the official test period, collect and use the following data to calculate average space heating capacity and electrical power. During heating and defrosting intervals when the controls of the heat pump have the indoor fan on, continuously record the dry-bulb temperature of the air entering (as noted above) and leaving the indoor coil. If using a thermopile, continuously record the difference between the leaving and entering dry-bulb temperatures during the interval(s) that air flows through the indoor coil. For heat pumps tested without an indoor fan installed, determine the corresponding cumulative time (in hours) of indoor coil airflow, Δτ_a. Sample measurements used in calculating the air volume rate (refer to sections 7.8.3.1 and 7.8.3.2 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22)) at equal intervals that span 10 minutes or less. Record the electrical energy consumed, expressed in watt-hours, from defrost termination to defrost termination, e_DEF^k(35), as well as the corresponding elapsed time in hours, Δτ_FR.

3.9.1  Average space heating capacity and electrical power calculations. a. Evaluate average space heating capacity, Q _h^k(35), when expressed in units of Btu per hour, using:

where,

V = the average indoor air volume rate measured during Sub-interval H, cfm.

C_p,a = 0.24 + 0.444 · W_n, the constant pressure specific heat of the air-water vapor mixture that flows through the indoor coil and is expressed on a dry air basis, Btu / lbm_da · °F.

v_n' = specific volume of the air-water vapor mixture at the nozzle, ft³ / lbm_mx.

W_n = humidity ratio of the air-water vapor mixture at the nozzle, lbm of water vapor per lbm of dry air.

Δτ_FR = τ₂ − τ₁, the elapsed time from defrost termination to defrost termination, hr.

T_al(τ) = dry bulb temperature of the air entering the indoor coil at elapsed time τ, °F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor fan cycles off.

T_a2(τ) = dry bulb temperature of the air leaving the indoor coil at elapsed time τ, °F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor fan cycles off.

τ₁ = the elapsed time when the defrost termination occurs that begins the official test period, hr.

τ₂ = the elapsed time when the next automatically occurring defrost termination occurs, thus ending the official test period, hr.

v_n = specific volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor content, and barometric pressure existing at the nozzle, ft³ per lbm of dry air.

b. Evaluate average electrical power, E _h^k(35), when expressed in units of watts, using:

For heat pumps tested without an indoor fan installed, increase Q _h^k(35) by,

and increase E _h^k(35) by,

where V _s is the average indoor air volume rate measured during the Frost Accumulation heating mode test and is expressed in units of cubic feet per minute of standard air (scfm).

c. For heat pumps having a constant-air-volume-rate indoor fan, the five additional steps listed below are required if the average of the external static pressures measured during sub-Interval H exceeds the applicable section 3.1.4.4, 3.1.4.5, or 3.1.4.6 minimum (or targeted) external static pressure (ΔP_min) by 0.03 inches of water or more:

1. Measure the average power consumption of the indoor fan motor (E _fan,1) and record the corresponding external static pressure (ΔP₁) during or immediately following the Frost Accumulation heating mode test. Make the measurement at a time when the heat pump is heating, except for the first 10 minutes after the termination of a defrost cycle.

2. After the Frost Accumulation heating mode test is completed and while maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP₁ + (ΔP₁ − ΔP_min).

3. After re-establishing steady readings for the fan motor power and external static pressure, determine average values for the indoor fan power (E _fan,2) and the external static pressure (ΔP₂) by making measurements over a 5-minute interval.

4. Approximate the average power consumption of the indoor fan motor had the Frost Accumulation heating mode test been conducted at ΔP_min using linear extrapolation:

5. Decrease the total heating capacity, Q _h^k(35), by the quantity [(E _fan,1 − E _fan,min)· (Δτ _a/Δτ _FR], when expressed on a Btu/h basis. Decrease the total electrical power, E_h^k(35), by the same quantity, now expressed in watts.

3.9.2  Demand defrost credit. a. Assign the demand defrost credit, F_def, that is used in section 4.2 to the value of 1 in all cases except for heat pumps having a demand-defrost control system (Definition 1.21). For such qualifying heat pumps, evaluate F_def using,

where,

Δτ_def = the time between defrost terminations (in hours) or 1.5, whichever is greater.

Δτ_max = maximum time between defrosts as allowed by the controls (in hours) or 12, whichever is less.

b. For two-capacity heat pumps and for section 3.6.2 units, evaluate the above equation using the Δτ_def that applies based on the Frost Accumulation Test conducted at high capacity and/or at the Heating Certified Air Volume Rate. For variable-speed heat pumps, evaluate Δτ_def based on the required Frost Accumulation Test conducted at the intermediate compressor speed.

3.10  Test procedures for steady-state Low Temperature heating mode tests (the H3, H3₂, and H3₁ Tests). Except for the modifications noted in this section, conduct the Low Temperature heating mode test using the same approach as specified in section 3.7 for the Maximum and High Temperature tests. After satisfying the section 3.7 requirements for the pretest interval but before beginning to collect data to determine Q _h^k(17) and E _h^k(17), conduct a defrost cycle. This defrost cycle may be manually or automatically initiated. The defrost sequence must be terminated by the action of the heat pump's defrost controls. Begin the 30-minute data collection interval described in section 3.7, from which Q _h^k(17) and E _h^k(17) are determined, no sooner than 10 minutes after defrost termination. Defrosts should be prevented over the 30-minute data collection interval.

3.11  Additional requirements for the secondary test methods. Prior to evaluating if the energy balance specified in section 3.1.1 is obtained, make an adjustment to account for the energy loss within the air duct that connects the indoor coil and the location where the outlet dry-bulb temperature is measured. If using the Outdoor Air Enthalpy Method, make an adjustment to account for the energy loss within the air duct that connects the outdoor coil and the location where the outlet temperature is measured. In all cases, apply the correction to the indoor space conditioning capacity that is determined using the secondary test method.

3.11.1  If using the Outdoor Air Enthalpy Method as the secondary test method. During the “official” test, the outdoor air-side test apparatus described in section 2.10.1 is connected to the outdoor unit. To help compensate for any effect that the addition of this test apparatus may have on the unit's performance, conduct a “preliminary” test where the outdoor air-side test apparatus is disconnected. Conduct a preliminary test prior to the first section 3.2 steady-state cooling mode test and prior to the first section 3.6 steady-state heating mode test. No other preliminary tests are required so long as the unit operates the outdoor fan during all cooling mode steady-state tests at the same speed and all heating mode steady-state tests at the same speed. If using more than one outdoor fan speed for the cooling mode steady-state tests, however, conduct a preliminary test prior to each cooling mode test where a different fan speed is first used. This same requirement applies for the heating mode tests.

3.11.1.1  If a preliminary test precedes the official test. a. The test conditions for the preliminary test are the same as specified for the official test. Connect the indoor air-side test apparatus to the indoor coil; disconnect the outdoor air-side test apparatus. Allow the test room reconditioning apparatus and the unit being tested to operate for at least one hour. After attaining equilibrium conditions, measure the following quantities at equal intervals that span 10 minutes or less:

1. The section 2.10.1 evaporator and condenser temperatures or pressures;

2. Parameters required according to the Indoor Air Enthalpy Method.

Continue these measurements until a 30-minute period (e.g., four consecutive 10-minute samples) is obtained where the Table 7 or Table 13, whichever applies, test tolerances are satisfied.

b. After collecting 30 minutes of steady-state data, reconnect the outdoor air-side test apparatus to the unit. Adjust the exhaust fan of the outdoor airflow measuring apparatus until averages for the evaporator and condenser temperatures, or the saturated temperatures corresponding to the measured pressures, agree within ±0.5 °F of the averages achieved when the outdoor air-side test apparatus was disconnected. Calculate the averages for the reconnected case using five or more consecutive readings taken at one minute intervals. Make these consecutive readings after re-establishing equilibrium conditions and before initiating the official test.

3.11.1.2  If a preliminary test does not precede the official test. Connect the outdoor-side test apparatus to the unit. Adjust the exhaust fan of the outdoor airflow measuring apparatus to achieve the same external static pressure as measured during the prior preliminary test conducted with the unit operating in the same cooling or heating mode at the same outdoor fan speed.

3.11.1.3  Official test. a. Continue (preliminary test was conducted) or begin (no preliminary test) the official test by making measurements for both the Indoor and Outdoor Air Enthalpy Methods at equal intervals that span 10 minutes or less. Discontinue these measurement only after obtaining a 30-minute period where the specified test condition and test operating tolerances are satisfied. To constitute a valid official test:

(1) Achieve the energy balance specified in section 3.1.1; and,

(2) For cases where a preliminary test is conducted, the capacities determined using the Indoor Air Enthalpy Method from the official and preliminary test periods must agree within 2.0 percent.

b. For space cooling tests, calculate capacity from the outdoor air enthalpy measurements as specified in section 7.3.3.2 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). Calculate heating capacity based on outdoor air enthalpy measurements as specified in section 7.3.4.2 of the same ASHRAE Standard. Adjust outdoor side capacities according to section 7.3.3.3 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22) to account for line losses when testing split systems. Do not correct the average electrical power measurement as described in section 8.5.3 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22).

3.11.2  If using the Compressor Calibration Method as the secondary test method.

a. Conduct separate calibration tests using a calorimeter to determine the refrigerant flow rate. Or for cases where the superheat of the refrigerant leaving the evaporator is less than 5 °F, use the calorimeter to measure total capacity rather than refrigerant flow rate. Conduct these calibration tests at the same test conditions as specified for the tests in this Appendix. Operate the unit for at least one hour or until obtaining equilibrium conditions before collecting data that will be used in determining the average refrigerant flow rate or total capacity. Sample the data at equal intervals that span 10 minutes or less. Determine average flow rate or average capacity from data sampled over a 30-minute period where the Table 7 (cooling) or the Table 13 (heating) tolerances are satisfied. Otherwise, conduct the calibration tests according to ASHRAE Standard 23–93 (incorporated by reference, see §430.22), ASHRAE Standard 41.9–00 (incorporated by reference, see §430.22), and section 7.5 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22).

b. Calculate space cooling and space heating capacities using the compressor calibration method measurements as specified in sections 7.5.7 and 7.5.8, respectively, of ASHRAE Standard 37–88 (incorporated by reference, see §430.22).

3.11.3  If using the Refrigerant Enthalpy Method as the secondary test method. Conduct this secondary method according to section 7.6 of ASHRAE Standard 37–88 (incorporated by reference, see §430.22). Calculate space cooling and space heating capacities using the refrigerant enthalpy method measurements as specified in sections 7.6.4 and 7.6.5, respectively, of the same ASHRAE Standard.

3.12  Rounding of space conditioning capacities for reporting purposes.

a. When reporting rated capacities, round them off as follows:

1. For capacities less than 20,000 Btu/h, round to the nearest 100 Btu/h.

2. For capacities between 20,000 and 37,999 Btu/h, round to the nearest 200 Btu/h.

3. For capacities between 38,000 and 64,999 Btu/h, round to the nearest 500 Btu/h.

b. For the capacities used to perform the section 4 calculations, however, round only to the nearest integer.

4. CALCULATIONS OF SEASONAL PERFORMANCE DESCRIPTORS

4.1  Seasonal Energy Efficiency Ratio (SEER) Calculations. SEER must be calculated as follows: For equipment covered under sections 4.1.2, 4.1.3, and 4.1.4, evaluate the seasonal energy efficiency ratio,

where,

the ratio of the total space cooling provided during periods of the space cooling season when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the cooling season (N), Btu/h.

the electrical energy consumed by the test unit during periods of the space cooling season when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the cooling season (N), W.

T_j = the outdoor bin temperature, °F. Outdoor temperatures are grouped or “binned.” Use bins of 5 °F with the 8 cooling season bin temperatures being 67, 72, 77, 82, 87, 92, 97, and 102 °F.

j = the bin number. For cooling season calculations, j ranges from 1 to 8.

Additionally, for sections 4.1.2, 4.1.3, and 4.1.4, use a building cooling load, BL(T_j). When referenced, evaluate BL(T_j) for cooling using,

where,

Q _ck=2(95) = the space cooling capacity determined from the A₂ Test and calculated as specified in section 3.3, Btu/h.

1.1 = sizing factor, dimensionless.

The temperatures 95 °F and 65 °F in the building load equation represent the selected outdoor design temperature and the zero-load base temperature, respectively.

4.1.1  SEER calculations for an air conditioner or heat pump having a single-speed compressor that was tested with a fixed-speed indoor fan installed, a constant-air-volume-rate indoor fan installed, or with no indoor fan installed. a. Evaluate the seasonal energy efficiency ratio, expressed in units of Btu/watt-hour, using:

SEER = PLF(0.5) · EER_B

where,

the energy efficiency ratio determined from the B Test described in sections 3.2.1, 3.1.4.1, and 3.3, Btu/h per watt.

PLF(0.5) = 1 − 0.5 · C_D^c, the part-load performance factor evaluated at a cooling load factor of 0.5, dimensionless.

b. Refer to section 3.3 regarding the definition and calculation of Q _c(82) and E _c(82). If the optional tests described in section 3.2.1 are not conducted, set the cooling mode cyclic degradation coefficient, C_D^c, to the default value specified in section 3.5.3. If these optional tests are conducted, set C_D^c to the lower of:

1. The value calculated as per section 3.5.3; or

2. The section 3.5.3 default value of 0.25.

4.1.2  SEER calculations for an air conditioner or heat pump having a single-speed compressor and a variable-speed variable-air-volume-rate indoor fan.

4.1.2.1  Units covered by section 3.2.2.1 where indoor fan capacity modulation correlates with the outdoor dry bulb temperature. The manufacturer must provide information on how the indoor air volume rate or the indoor fan speed varies over the outdoor temperature range of 67 °F to 102 °F. Calculate SEER using Equation 4.1–1. Evaluate the quantity q_c(T_j)/N in Equation 4.1–1 using,

where,

whichever is less; the cooling mode load factor for temperature bin j, dimensionless.

Q _c(T_j) = the space cooling capacity of the test unit when operating at outdoor temperature, T_j, Btu/h.

n_j/N = fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the cooling season, dimensionless.

a. For the space cooling season, assign n_j/N as specified in Table 16. Use Equation 4.1–2 to calculate the building load, BL(T_j). Evaluate Q _c(T_j) using,

where,

the space cooling capacity of the test unit at outdoor temperature T_j if operated at the Cooling Minimum Air Volume Rate, Btu/h.

the space cooling capacity of the test unit at outdoor temperature T_j if operated at the Cooling Certified Air Volume Rate, Btu/h.

b. For units where indoor fan speed is the primary control variable, FP_ck=1 denotes the fan speed used during the required A₁ and B₁ Tests (see section 3.2.2.1), FP_ck=2 denotes the fan speed used during the required A₂ and B₂ Tests, and FP_c(T_j) denotes the fan speed used by the unit when the outdoor temperature equals T_j. For units where indoor air volume rate is the primary control variable, the three FP_c's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 regarding the definitions and calculations of Q _ck=1(82), Q _ck=1(95),Q _c k=2(82), and Q _ck=2(95).

Calculate e_c(T_j)/N in Equation 4.1–1 using,

where,

PLF_j = 1 − C_D^c · [1 − X(T_j)], the part load factor, dimensionless.

E _c(T_j) = the electrical power consumption of the test unit when operating at outdoor temperature T_j, W.

c. The quantities X(T_j) and n_j /N are the same quantities as used in Equation 4.1.2–1. If the optional tests described in section 3.2.2.1 and Table 4 are not conducted, set the cooling mode cyclic degradation coefficient, C_D^c, to the default value specified in section 3.5.3. If these optional tests are conducted, set C_D^c to the lower of:

1. The value calculated as per section 3.5.3; or

2.The section 3.5.3 default value of 0.25.

d. Evaluate E _c(T_j) using,

where

the electrical power consumption of the test unit at outdoor temperature T_j if operated at the Cooling Minimum Air Volume Rate, W.

the electrical power consumption of the test unit at outdoor temperature T_j if operated at the Cooling Certified Air Volume Rate, W.

e. The parameters FP_ck=1, and FP_ck=2, and FP_c(T_j) are the same quantities that are used when evaluating Equation 4.1.2–2. Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 regarding the definitions and calculations of E _ck=1(82), E _ck=1(95), E _ck=2(82), and E _ck=2(95).

4.1.2.2  Units covered by section 3.2.2.2 where indoor fan capacity modulation is used to adjust the sensible to total cooling capacity ratio. Calculate SEER as specified in section 4.1.1.

4.1.3  SEER calculations for an air conditioner or heat pump having a two-capacity compressor. Calculate SEER using Equation 4.1–1. Evaluate the space cooling capacity, Q _ck=1(T_j), and electrical power consumption, E _ck=1(T_j), of the test unit when operating at low compressor capacity and outdoor temperature T_j using,

where Q _ck=1(95) and E _ck=1(95) are determined from the A₁ Test, Q _ck=1(82) and E _ck=1(82) are determined from the B₁ Test, and all are calculated as specified in section 3.3. For two-capacity units that lock out low capacity operation at outdoor temperatures less than 95°F (but greater than 82°F), use Equations 4.1.4–1 and 4.1.4–2 rather than Equations 4.1.3–1 and 4.1.3–2 for estimating performance at low compressor capacity. Evaluate the space cooling capacity, Q _ck=2(T_j), and electrical power consumption, E _ck=2(T_j), of the test unit when operating at high compressor capacity and outdoor temperature T_j using,

where Q _ck=2(95) and E _ck=2(95) are determined from the A₂ Test, Q _ck=2(82), and E _ck=2(82), are determined from the B₂ Test, and all are calculated as specified in section 3.3.

The calculation of Equation 4.1–1 quantities q_c(T_j)/N and e_c(T_j)/N differs depending on whether the test unit would operate at low capacity (section 4.1.3.1), cycle between low and high capacity (section 4.1.3.2), or operate at high capacity (sections 4.1.3.3 and 4.1.3.4) in responding to the building load. For units that lock out low capacity operation at higher outdoor temperatures, the manufacturer must supply information regarding this temperature so that the appropriate equations are used. Use Equation 4.1–2 to calculate the building load, BL(T_j), for each temperature bin.

4.1.3.1  Steady-state space cooling capacity at low compressor capacity is greater than or equal to the building cooling load at temperature T_j, Q _ck=1(T_j) ≥ BL(T_j).

where,

Xk=1(T_j) = BL(T_j)/Q _ck=1(T_j), the cooling mode low capacity load factor for temperature bin j, dimensionless.

PLF_j = 1 − C_D^c · [1 − Xk=1(T_j)], the part load factor, dimensionless.

fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the cooling season, dimensionless.

Obtain the fractional bin hours for the cooling season, n_j/N, from Table 16. Use Equations 4.1.3–1 and 4.1.3–2, respectively, to evaluate Q _ck=1(T_j) and E _ck=1(T_j). If the optional tests described in section 3.2.3 and Table 5 are not conducted, set the cooling mode cyclic degradation coefficient, C_D^c, to the default value specified in section 3.5.3. If these optional tests are conducted, set C_D^c to the lower of:

a. The value calculated according to section 3.5.3; or

b. The section 3.5.3 default value of 0.25.

4.1.3.2  Unit alternates between high (k=2) and low (k=1) compressor capacity to satisfy the building cooling load at temperature T_j, Q _ck=1(T_j) < BL(T_j) < Q _ck=2(T_j).

where,

the cooling mode, low capacity load factor for temperature bin j, dimensionless.

Xk=2(T_j) = 1 − Xk=1(T_j), the cooling mode, high capacity load factor for temperature bin j, dimensionless.

Obtain the fractional bin hours for the cooling season, n_j/N, from Table 16. Use Equations 4.1.3–1 and 4.1.3–2, respectively, to evaluate Q _ck=1(T_j) and E _ck=1(T_j). Use Equations 4.1.3–3 and 4.1.3–4, respectively, to evaluate Q _ck=2(T_j) and E _ck=2(T_j).

4.1.3.3  Unit only operates at high (k=2) compressor capacity at temperature T_j and its capacity is greater than the building cooling load, BL(T_j) < Q _ck=2(T_j). This section applies to units that lock out low compressor capacity operation at higher outdoor temperatures.

where,

Xk=2(T_j) = BL(T_j)/Q _ck=2(T_j), the cooling mode high capacity load factor for temperature bin j, dimensionless.

PLF_j = 1 − C_D^c · [1 − Xk=2(T_j)], the part load factor, dimensionless.

Obtain the fractional bin hours for the cooling season, n_j/N, from Table 16. Use Equations 4.1.3–3 and 4.1.3–4, respectively, to evaluate Q _ck=2(T_j) and E _ck=2(T_j). When evaluating the above equation for part load factor at high capacity, use the same value of C_D^c as used in the section 4.1.3.1 calculations.

4.1.3.4  Unit must operate continuously at high (k=2) compressor capacity at temperature T_j, BL(T_j) ≥ Q _ck=2(T_j).

Obtain the fractional bin hours for the cooling season, n_j/N, from Table 16. Use Equations 4.1.3–3 and 4.1.3–4, respectively, to evaluate Q _ck=2(T_j) and E _ck=2(T_j).

4.1.4  SEER calculations for an air conditioner or heat pump having a variable-speed compressor. Calculate SEER using Equation 4.1–1. Evaluate the space cooling capacity, Q _ck=1(T_j), and electrical power consumption, E _ck=1(T_j), of the test unit when operating at minimum compressor speed and outdoor temperature T_j. Use,

where Q _ck=1(82) and E _ck=1(82) are determined from the B₁ Test, Q _ck=1(67) and E _ck=1(67) are determined from the F1 Test, and all four quantities are calculated as specified in section 3.3. Evaluate the space cooling capacity, Q _ck=2(T_j), and electrical power consumption, E _ck=2(T_j), of the test unit when operating at maximum compressor speed and outdoor temperature T_j. Use Equations 4.1.3–3 and 4.1.3–4, respectively, where Q _ck=2(95) and E _ck=2(95) are determined from the A₂ Test, Q _ck=2(82) and E _ck=2(82) are determined from the B₂ Test, and all four quantities are calculated as specified in section 3.3. Calculate the space cooling capacity, Q _ck=v(T_j), and electrical power consumption, E _ck=v(T_j), of the test unit when operating at outdoor temperature T_j and the intermediate compressor speed used during the section 3.2.4 (and Table 6) E_V Test using,

where Q _ck=v(87) and E _ck=v(87) are determined from the E_V Test and calculated as specified in section 3.3. Approximate the slopes of the k = v intermediate speed cooling capacity and electrical power input curves, M_Q and M_E, as follows:

where,

Calculating Equation 4.1–1 quantities

differs depending upon whether the test unit would operate at minimum speed (section 4.1.4.1), operate at an intermediate speed (section 4.1.4.2), or operate at maximum speed (section 4.1.4.3) in responding to the building load. Use Equation 4.1–2 to calculate the building load, BL(T_j), for each temperature bin.

4.1.4.1  Steady-state space cooling capacity when operating at minimum compressor speed is greater than or equal to the building cooling load at temperature T_j, Q _ck=1(T_j) ≥ BL(T_j).

where,

Xk=1(T_j) = BL(T_j) / Q _ck=1(T_j), the cooling mode minimum speed load factor for temperature bin j, dimensionless.

PLF_j = 1 − C_D^c · [1 − Xk=1(T_j)], the part load factor, dimensionless.

n_j/N = fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the cooling season, dimensionless.

Obtain the fractional bin hours for the cooling season, n_j/N, from Table 16. Use Equations 4.1.4–1 and 4.1.4–2, respectively, to evaluate Q _ck=1(T_j) and E _ck=1(T_j). If the optional tests described in section 3.2.4 and Table 6 are not conducted, set the cooling mode cyclic degradation coefficient, C_D^c, to the default value specified in section 3.5.3. If these optional tests are conducted, set C_D^c to the lower of:

a. The value calculated according to section 3.5.3; or

b. The section 3.5.3 default value of 0.25.

4.1.4.2  Unit operates at an intermediate compressor speed (k=i) in order to match the building cooling load at temperature T_j,Q _ck=1(T_j) < BL(T_j) < Q _ck=2(T_j).

where,

Q _ck=i(T_j) = BL(T_j), the space cooling capacity delivered by the unit in matching the building load at temperature T_j, Btu/h. The matching occurs with the unit operating at compressor speed k = i.

the electrical power input required by the test unit when operating at a compressor speed of k = i and temperature T_j, W.

EERk=i(T_j) = the steady-state energy efficiency ratio of the test unit when operating at a compressor speed of k = i and temperature T_j, Btu/h per W.

Obtain the fractional bin hours for the cooling season, n_j/N, from Table 16. For each temperature bin where the unit operates at an intermediate compressor speed, determine the energy efficiency ratio EERk=i(T_j) using,

EERk=i(T_j) = A + B · T_j + C · T_j² .

For each unit, determine the coefficients A, B, and C by conducting the following calculations once:

where,

T_l = the outdoor temperature at which the unit, when operating at minimum compressor speed, provides a space cooling capacity that is equal to the building load (Q _ck=1(T₁) = BL(T₁)), °F. Determine T₁ by equating Equations 4.1.4–1 and 4.1–2 and solving for outdoor temperature.

T_v = the outdoor temperature at which the unit, when operating at the intermediate compressor speed used during the section 3.2.4 E_V Test, provides a space cooling capacity that is equal to the building load (Q _ck=v (T_v) = BL(T_v)), °F. Determine T_v by equating Equations 4.1.4–3 and 4.1–2 and solving for outdoor temperature.

T₂ = the outdoor temperature at which the unit, when operating at maximum compressor speed, provides a space cooling capacity that is equal to the building load (Q _ck=2 (T₂) = BL(T₂)), °F. Determine T₂ by equating Equations 4.1.3–3 and 4.1–2 and solving for outdoor temperature.

4.1.4.3  Unit must operate continuously at maximum (k=2) compressor speed at temperature Tj, BL(T_j) ≥ Q _ck=2(T_j). Evaluate the Equation 4.1–1 quantities

as specified in section 4.1.3.4 with the understanding that Q _ck=2(T_j) and E _ck=2(T_j) correspond to maximum compressor speed operation and are derived from the results of the tests specified in section 3.2.4.

4.2  Heating Seasonal Performance Factor (HSPF) Calculations. Unless an approved alternative rating method is used, as set forth in 10 CFR 430.24(m), Subpart B, HSPF must be calculated as follows: Six generalized climatic regions are depicted in Figure 2 and otherwise defined in Table 17. For each of these regions and for each applicable standardized design heating requirement, evaluate the heating seasonal performance factor using,

where,

e_h(T_j)/N=

The ratio of the electrical energy consumed by the heat pump during periods of the space heating season when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the heating season (N), W. For heat pumps having a heat comfort controller, this ratio may also include electrical energy used by resistive elements to maintain a minimum air delivery temperature (see 4.2.5).

RH(T_j)/N=

The ratio of the electrical energy used for resistive space heating during periods when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the heating season (N),W. Except as noted in section 4.2.5, resistive space heating is modeled as being used to meet that portion of the building load that the heat pump does not meet because of insufficient capacity or because the heat pump automatically turns off at the lowest outdoor temperatures. For heat pumps having a heat comfort controller, all or part of the electrical energy used by resistive heaters at a particular bin temperature may be reflected in e_h(T_j)/N (see 4.2.5).

T_j = the outdoor bin temperature, °F. Outdoor temperatures are “binned” such that calculations are only performed based one temperature within the bin. Bins of 5 °F are used.

n_j/N=

Fractional bin hours for the heating season; the ratio of the number of hours during the heating season when the outdoor temperature fell within the range represented by bin temperature T_j to the total number of hours in the heating season, dimensionless. Obtain n_j/N values from Table 17.

j = the bin number, dimensionless.

J = for each generalized climatic region, the total number of temperature bins, dimensionless. Referring to Table 17, J is the highest bin number (j) having a nonzero entry for the fractional bin hours for the generalized climatic region of interest.

F_def = the demand defrost credit described in section 3.9.2, dimensionless.

BL(T_j) = the building space conditioning load corresponding to an outdoor temperature of T_j; the heating season building load also depends on the generalized climatic region's outdoor design temperature and the design heating requirement, Btu/h.

Evaluate the building heating load using

where,

T_OD = the outdoor design temperature, °F. An outdoor design temperature is specified for each generalized climatic region in Table 17.

C = 0.77, a correction factor which tends to improve the agreement between calculated and measured building loads, dimensionless.

DHR = the design heating requirement (see Definition 1.22), Btu/h.

Calculate the minimum and maximum design heating requirements for each generalized climatic region as follows:

and

where Q _h^k(47) is expressed in units of Btu/h and otherwise defined as follows:

1. For a single-speed heat pump tested as per section 3.6.1, Q _h^k(47) = Q _h(47), the space heating capacity determined from the H1 Test.

2. For a variable-speed heat pump, a section 3.6.2 single-speed heat pump, or a two-capacity heat pump not covered by item 3, Q _n^k(47) = Q _nk=2(47), the space heating capacity determined from the H1₂ Test.

3. For two-capacity, northern heat pumps (see Definition 1.46), Q ^k_h(47) = Q k=1_h(47), the space heating capacity determined from the H1₁ Test.

If the optional H1_N Test is conducted on a variable-speed heat pump, the manufacturer has the option of defining Q ^k_h(47) as specified above in item 2 or as Q ^k_h(47)=Q k=N_h(47), the space heating capacity determined from the H1_N Test.

For all heat pumps, HSPF accounts for the heating delivered and the energy consumed by auxiliary resistive elements when operating below the balance point. This condition occurs when the building load exceeds the space heating capacity of the heat pump condenser. For HSPF calculations for all heat pumps, see either section 4.2.1, 4.2.2, 4.2.3, or 4.2.4, whichever applies.

For heat pumps with heat comfort controllers (see Definition 1.28), HSPF also accounts for resistive heating contributed when operating above the heat-pump-plus-comfort-controller balance point as a result of maintaining a minimum supply temperature. For heat pumps having a heat comfort controller, see section 4.2.5 for the additional steps required for calculating the HSPF.

4.2.1  Additional steps for calculating the HSPF of a heat pump having a single-speed compressor that was tested with a fixed-speed indoor fan installed, a constant-air-volume-rate indoor fan installed, or with no indoor fan installed.

where,

whichever is less; the heating mode load factor for temperature bin j, dimensionless.

Q _h(T_j) = the space heating capacity of the heat pump when operating at outdoor temperature T_j, Btu/h.

E _h(T_j) = the electrical power consumption of the heat pump when operating at outdoor temperature T_j, W.

δ(T_j) = the heat pump low temperature cut-out factor, dimensionless.

PLF_j = 1 − C _D^h · [1 −X(T_j)] the part load factor, dimensionless.

Use Equation 4.2–2 to determine BL(T_j). Obtain fractional bin hours for the heating season, n_j/N, from Table 17. If the optional H1C Test described in section 3.6.1 is not conducted, set the heating mode cyclic degradation coefficient, C_D^h, to the default value specified in section 3.8.1. If this optional test is conducted, set C _D^h to the lower of:

a. The value calculated according to section 3.8.1 or

b. The section 3.8.1 default value of 0.25.

Determine the low temperature cut-out factor using

where,

T_off = the outdoor temperature when the compressor is automatically shut off, °F. (If no such temperature exists, T_j is always greater than T_off and T_on).

T_on = the outdoor temperature when the compressor is automatically turned back on, if applicable, following an automatic shut-off, °F.

Calculate Q _h(T_j) and E _h(T_j) using,

where Q _h(47) and E _h(47) are determined from the H1 Test and calculated as specified in section 3.7; Q _h(35) and E _h(35) are determined from the H2 Test and calculated as specified in section 3.9.1; and Q _h(17) and E _h(17) are determined from the H3 Test and calculated as specified in section 3.10.

4.2.2  Additional steps for calculating the HSPF of a heat pump having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor fan. The manufacturer must provide information about how the indoor air volume rate or the indoor fan speed varies over the outdoor temperature range of 65 °F to −23 °F. Calculate the quantities

in Equation 4.2–1 as specified in section 4.2.1 with the exception of replacing references to the H1C Test and section 3.6.1 with the H1C₁ Test and section 3.6.2. In addition, evaluate the space heating capacity and electrical power consumption of the heat pump Q _h(T_j) and E _h(T_j) using

where the space heating capacity and electrical power consumption at both low capacity (k=1) and high capacity (k=2) at outdoor temperature Tj are determined using

For units where indoor fan speed is the primary control variable, FP_hk=1 denotes the fan speed used during the required H1₁ and H3₁ Tests (see Table 10), FP_hk=2 denotes the fan speed used during the required H1₂, H2₂, and H3₂ Tests, and FP_h(T_j) denotes the fan speed used by the unit when the outdoor temperature equals T_j. For units where indoor air volume rate is the primary control variable, the three FP_h's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Determine Q _hk=1(47) and E _hk=1(47) from the H1₁ Test, and Q _hk=2(47) and E _hk=2(47) from the H1₂ Test. Calculate all four quantities as specified in section 3.7. Determine Q _hk=1(35) and E _hk=1(35) as specified in section 3.6.2; determine Q _hk=2(35) and E _hk=2(35) and from the H2₂ Test and the calculation specified in section 3.9. Determine Q _hk=1(17) and E _hk=1(17 from the H3₁ Test, and Q _hk=2(17) and E _hk=2(17) from the H3₂ Test. Calculate all four quantities as specified in section 3.10.

4.2.3  Additional steps for calculating the HSPF of a heat pump having a two-capacity compressor. The calculation of the Equation 4.2–1 quantities

differs depending upon whether the heat pump would operate at low capacity (section 4.2.3.1), cycle between low and high capacity (Section 4.2.3.2), or operate at high capacity (sections 4.2.3.3 and 4.2.3.4) in responding to the building load. For heat pumps that lock out low capacity operation at low outdoor temperatures, the manufacturer must supply information regarding the cutoff temperature(s) so that the appropriate equations can be selected.

a. Evaluate the space heating capacity and electrical power consumption of the heat pump when operating at low compressor capacity and outdoor temperature T_j using

b. Evaluate the space heating capacity and electrical power consumption (Q _hk=2(T_j) and E _hk=2 (T_j)) of the heat pump when operating at high compressor capacity and outdoor temperature Tj by solving Equations 4.2.2–3 and 4.2.2–4, respectively, for k=2. Determine Q _hk=1(62) and E _hk=1(62) from the H0₁ Test, Q _hk=1(47) and E _hk=1(47) from the H1₁ Test, and Q _hk=2(47) and E _hk=2(47) from the H1₂ Test. Calculate all six quantities as specified in section 3.7. Determine Q _hk=2(35) and E _hk=2(35) from the H2₂ Test and, if required as described in section 3.6.3, determine Q _hk=1(35) and E _hk=1(35) from the H2₁ Test. Calculate the required 35 °F quantities as specified in section 3.9. Determine Q _hk=2(17) and E _hk=2(17) from the H3₂ Test and, if required as described in section 3.6.3, determine Q _hk=1(17) and E _hk=1(17) from the H3₁ Test. Calculate the required 17 °F quantities as specified in section 3.10.